EP1170512A1 - Vérin à fluide sous pression avec verrouillage mécanique lorsque non pressurisé - Google Patents

Vérin à fluide sous pression avec verrouillage mécanique lorsque non pressurisé Download PDF

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Publication number
EP1170512A1
EP1170512A1 EP01114451A EP01114451A EP1170512A1 EP 1170512 A1 EP1170512 A1 EP 1170512A1 EP 01114451 A EP01114451 A EP 01114451A EP 01114451 A EP01114451 A EP 01114451A EP 1170512 A1 EP1170512 A1 EP 1170512A1
Authority
EP
European Patent Office
Prior art keywords
piston
locking
working cylinder
unlocking
thread
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
EP01114451A
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German (de)
English (en)
Other versions
EP1170512B1 (fr
Inventor
Josef Büter
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Buemach Engineering International BV
Original Assignee
Buemach Engineering International BV
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Filing date
Publication date
Application filed by Buemach Engineering International BV filed Critical Buemach Engineering International BV
Publication of EP1170512A1 publication Critical patent/EP1170512A1/fr
Application granted granted Critical
Publication of EP1170512B1 publication Critical patent/EP1170512B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/26—Locking mechanisms
    • F15B15/261—Locking mechanisms using positive interengagement, e.g. balls and grooves, for locking in the end positions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/26—Locking mechanisms
    • F15B15/262—Locking mechanisms using friction, e.g. brake pads
    • F15B15/264—Screw mechanisms attached to the piston

Definitions

  • the invention relates to a working cylinder with mechanical Path blocking for use in hydraulic or pneumatic operated mechanisms, their movement in the event of failure the pressure energy through a mechanical locking system is hindered.
  • a similar solution of a blocking clamping device is described in the document DE 38 11 225 C2.
  • Several axially displaceable clamping jaws are pressed against the piston rod by spring elements for blocking.
  • the opening position is achieved with a cylinder-guided servo piston.
  • a device for clamping an axially moving rod is also disclosed in DE 37 07 046 A1.
  • the clamping takes place by means of a clamping sleeve with an outer cone, on which the inner cone of a piston which is under spring preload acts.
  • the clamping heads described have in common that in the case of large dynamic forces that occur, precise positioning is generally not possible due to the static friction.
  • the clamping also has a disadvantageous effect on the service life of functional parts, here the piston rod, since considerable friction is caused by static friction.
  • the dimensions of a working cylinder with such clamping devices are considerably larger, or if the clamping devices are mounted outside the cylinder, they are radially wide.
  • the solution of a device for locking a piston rod of a piston-cylinder arrangement disclosed in the document DE 3810183 A1 has almost the same disadvantages of wearing functional parts.
  • the piston has disc segments which can be displaced by means of springs, which are pressed onto conical surfaces on the disc surfaces by means of annular, piston-like actuating elements with conical actuating elements and thus pull the disc segments inwards against the pressure of the springs.
  • a hollow piston rod with an internal profile in which a displaceable, axially spring-loaded rod with a ball circulation channel with balls which engage in the profile of the piston rod is arranged.
  • the rod is connected to an actuating piston in an actuating cylinder which, when pressurized with the pressure medium of the working cylinder, displaces the rod in such a way that the balls can circulate freely and, in the event of a pressure drop, are brought into the blocking position, thus preventing the piston rod from moving further.
  • the document DE 297 20 838 U1 describes a working cylinder with an integrated lifting brake, which essentially consists of a brake cone and a brake piston, a non-positive coupling being present between them in the depressurized state.
  • the brake cone is connected to a threaded spindle in the hollow piston rod, which is driven by the working piston movement by means of a spindle nut.
  • the brake piston with a compression spring in a spring chamber is arranged in the bottom closure part.
  • the pressure medium available for actuating the working cylinder is used by guiding it into the piston chamber of the brake piston via a 4/3 valve and a separate connection on the working cylinder and removing it from the brake cone against the spring preload. The pressure is applied to the brake piston and the working piston at the same time, so that the release is always carried out under load, without a force-free decoupling.
  • this version of a lifting brake with a frictional brake arranged in the vicinity of the central axis of the working cylinder, can only be used for very small locking torques.
  • a pneumatic working cylinder for presetting the cylinder with an active or passive brake is disclosed in EP 0 648 942 A1.
  • a threaded rod is arranged, which is connected to a brake disc, the rotation and thus the piston movement of which is braked or blocked by means of a friction element.
  • the friction element is located on a locking element made of two interconnected piston elements, which are slidably arranged in a separate piston chamber with its own connection for the pressure medium.
  • the brake can be designed as an active or passive brake during assembly of the working cylinder. An additional, separately controlled pressure medium connection is always required to release or actuate the brake.
  • the position of the working piston is evaluated using a signal generator coupled to the threaded rod.
  • a working cylinder Due to the type of design and the interaction of the brake disc and the friction element, such a working cylinder can likewise only be used expediently when the locking torque is low.
  • Another cylinder with locking means is described in the document US 2 804 053.
  • This also has a working piston with a hollow piston rod, spindle nut, threaded spindle and an axially displaceable brake part connected to it, in the form of a brake disc, which is spring-loaded in engagement with another brake part in the form of a friction element in the depressurized state.
  • a special release piston with plunger which lifts the brake disc from the friction element when pressure is applied, is arranged in an additional piston chamber with a separate pressure medium connection.
  • the threaded spindle can only rotate in one direction, step by step.
  • the two ratchet wheels are kept apart from each other by means of spring preload, a small piston rod of a special piston in a separate piston chamber using an spring arranged in this to cause the disk to move axially with the first ratchet wheel.
  • This spring is counteracted by a second spring with higher preload in a drilled piston chamber of a second special piston on the sliding ratchet wheel.
  • the second special piston is moved by the loose extension rod when the piston rod of the working cylinder is in a predetermined position when retracting, whereby the second special piston with the disk of the ratchet wheel moves until it engages with the fixed ratchet wheel and prevents the piston rod from extending again becomes.
  • the piston chamber of the special piston is first pressurized, so that the ratchet wheels in engagement are separated and only then is the cylinder chamber for extending the piston rod pressurized by means of a necessary hydraulic control.
  • the object of the invention is a pressure medium operated Working cylinders with mechanical path locking too develop, the locking device integrated in the working cylinder which is accurate positioning and instant reliable blocking in the event of pressure loss guaranteed, no additional auxiliary energy and additional external Control elements and control lines for the Ent and Locking also requires a compact design allows.
  • the basic idea of the invention consists in the formation of a working cylinder with integrated mechanical locking of the translational movement of a hollow piston rod, which is coupled to a pierced piston, the inside of the bore of the piston having a thread which has an external thread, inside the hollow Piston rod arranged threaded spindle is engaged with a coupling profile at its lower end, and on the coupling profile a movable locking disc, with a ring gear on the underside, is positively axially displaceably mounted with a ring gear on the top of a fixed locking disc in the bottom part of the working cylinder Formgehemme forms, and the sprockets of the movable and the fixed locking disk are positively coupled to each other in the depressurized state.
  • the toothed ring of the axially displaceable locking disk can advantageously be changed for repair purposes.
  • a non-self-locking thread with a large pitch is preferably used in order to enable smooth, free rotation of the threaded spindle, which is mounted in high-quality plain bearings.
  • the pitch of the thread determines the value of the resulting negative reverse torque depending on the value of the force acting on the piston rod and the friction values between the functional parts of the working cylinder.
  • the locking device is pressure-dependent. A control integrated in the base part of the working cylinder always puts it into the blocked state when there is no operating pressure of a fluid or the pressure fails.
  • the locking device When the working cylinder is subjected to the operating pressure, the locking device is first released by lifting the spring-loaded, axially movable locking disk with the ring gear by means of an unlocking piston via a plunger relative to the ring gear of the fixed locking disk, so that the main piston of the working cylinder can only move afterwards becomes.
  • the threaded spindle is rotated with the positively coupled, axially movable locking disk.
  • the cylinder chamber of the unlocking piston is also depressurized, whereby the spring-loaded, axially displaceable locking disk coupled with the threaded spindle and positively coupled presses the unlocking piston back over the plunger and presses it with the ring gear against the ring gear of the fixed locking disk, producing a positive coupling and the rotation the threaded spindle locks immediately.
  • the control integrated in the base part of the working cylinder which works for the mechanical locking system consisting essentially of the rotating threaded spindle and the form lock, works with the normal operating pressure of the working cylinder.
  • the control has a central slide with fluid return channels that can be displaced slightly by a central position against spring forces, which is in neutral neutral position when depressurized, these fluid return channels are connected to the unlocking piston chamber, depressurize the unlocking piston chamber so that the fluid caused by the unlocking is released flows into the respective flow-oriented connection via non-return valves and is pressed into its initial position by the spring preload of the axially movable locking disk and the tappets of the unlocking piston.
  • fluid under pressure first flows through the channels, which lead to the unlocking piston chamber and piston chamber of the working cylinder.
  • Check valves with a defined preload are installed in each of these channels, which initially prevent the outflow into the piston chambers, with the extent of the pressure increase first displacing the central slide into its end position and then pressurizing the unlocking piston.
  • the unlocking piston moves the movable locking disk against the action of the locking spring via plunger, so that the unlocked state is present.
  • the preload valves, which prevent the outflow of the fluid into the respective piston chamber are set 10% higher in their preload than the preloaded check valves, which prevent the free flow into the unlocking piston chamber. In this way, the safe guarantee for the onset of the movement of the piston is only given after the mold lock has been unlocked.
  • Check valves are connected in parallel to the preload valves, which lead to the piston chambers of the working cylinder, to allow the fluid to flow out of the respective piston chamber.
  • the cylinder tube is advantageously double-walled with channels on the inner tube, as a result of which the fluid is conducted to and from the piston rod space without additional external lines via the control in the base part of the working cylinder.
  • the size of the axial force of the spring for the pretensioning of the axially movable locking disk must be such that, with sufficient locking quality, taking into account the dynamic loads acting on the working cylinder, it corresponds at least to the return torque impressed by the external load.
  • the turning of the working cylinder is prevented by flattening the base part and corresponding counterparts at the installation location, or, in the case of a simple version, via the stub axle of the spherical bearings.
  • the size of the working cylinder with mechanical travel lock does not differ in the radial dimensions and in the axial dimensions only insignificantly from that of a comparable working cylinder without travel blocking.
  • a working cylinder 1 with its main axis 2 in a double-walled cylinder tube 3 with channels 4 and radial groove 5 has a piston 6 with an internal thread 7, which is coupled to a hollow piston rod 8.
  • a threaded spindle 9 protrudes into the hollow piston rod 8, at the lower end of which a square 10 is integrally formed for positive coupling with a displaceable locking disk 11 with a first toothed ring 12, which is pretensioned by means of a locking spring 13.
  • a bottom part 23 composed of several individual parts with an inflow connection 24, which is connected via an upper line 25 to an inner annular chamber 26 and an upper connecting line 27 with an upper check valve chamber 28 with an upper check valve 29;
  • a drain connection 30, which is connected to a space 31, via a lower connecting line 32, an outer ring channel 33 and a line 34 with an oil return valve with valve space 35, a central slide 36 is arranged for controlling the pressurization of the unlocking piston 15.
  • the central slide 36 is held in the depressurized state by springs 37 in the defined central position, with a connection between an unlocking piston chamber 40 and the check valves 29; via its return flow channels 38 and a return flow bore 39; 35 exists.
  • an upper blocking tube 41 In the bottom part 23 there are furthermore an upper blocking tube 41, an oil return-leading blocking tube 42, to which, according to FIGS. 5 and 6, a check valve 43 (43.1; 43.2) is connected antiparallel, which is connected via an annular chamber 44 and a bore 45 (45.1; 45.2) in the locking tube 41; 42 flows out, arranged. 1 and 2, the upper locking tube 41 is connected to the channels 4 in the double-walled cylinder tube 3 via a left-hand annular chamber 46 and lines 47 (47.1; 47.2) and thus further via the radial groove 5 to a piston rod space 48.
  • the oil return-leading locking tube 42 is connected to a piston chamber 50 via a further line 49.
  • FIG. 2 also shows the connections between the unlocking piston chamber 40 and the inner annular chamber 26 via an upper connecting channel 51 with a further pre-stressed check valve 52 and between the outer ring channel 33 via a lower connecting channel 53 with an additional pre-stressed check valve 54 and the unlocking piston chamber 40 , 4, the double-walled cylinder tube 3 with its channels 4 and the threaded spindle 9 with the axial bore 21 and the radial bores 22 connected to it are additionally shown.
  • the mechanically acting locking system in a double-acting working cylinder 1 lies in its main axis 2, the autonomous control being arranged in the base part 23 and being actuated for normal operation only by the pressure of the inflow and outflow of the fluid. It essentially consists of a threaded spindle 9, an axially displaceable locking disk 11 with a first ring gear 12, which is mounted on the square 10 such that it cannot rotate, with a positive fit, and a fixed locking disk 18 with a second ring gear 17.
  • the teeth are the first Gear ring 12 of the displaceable locking disk 11 and that of the second ring gear 17 of the fixed locking disk 18 in engagement, positively coupled, the displaceable locking disk 11 having been moved by means of the locking spring 13 into this locking position on the square 10.
  • the displaceable locking disk 11 and the fixed locking disk 18 with the ring gears 12; 17, the pairing of the thread of the threaded spindle 9 with the internal thread 7 of the piston 6 and the locking spring 13 are the decisive functional elements of the mechanical locking system, the latching, positive engagement of the teeth of the two ring gears 12; 17 works as a mold.
  • the fixed locking disk 18 can be detached from the base part 23 in a known manner, but is non-positively and positively connected. At a suitable point on the outer jacket of the base part 23, flats can be worked in, which ensure a rotationally secure external coupling of the working cylinder 1 when larger reverse torques can be safely absorbed. Smaller reverse torques can be guided over the axis of the working cylinder 1 in order to generate a counter torque via a thru-axle bearing connected to the piston rod 8.
  • State 1 the locked system is to be unlocked when the piston rod 8 is retracted by the inflow of a pressurized fluid.
  • the pressurized fluid is introduced via the inflow connection 24 and passes via the upper line 25 into the inner annular chamber 26, from which it passes further via the upper connecting line 27 into the upper check valve chamber 28, which enables the outflow into the upper shut-off tube 41.
  • the locking tubes 41; 42 each have a bias valve 55 (55.1; 55.2) on their left end.
  • the blocking tubes 41; 42 are the check valves 43.1; 43.2 switched antiparallel in order to enable the backflow from the respective run-oriented piston rod chamber 48 or piston chamber 50.
  • the preload of the preload valves 55.1; 55.2 is dimensioned such that there is a guarantee that the central slide 36, which is held in a non-pressurized state by the springs 37 in a defined central position, is pressed into its right-hand end position when the piston rod 8 is retracted before the preload valve 55.1 transfers the fluid the line 47.1, the channels 4 and the radial groove 5 can flow into the piston rod space 48. In the right-hand end position of the central slide 36, its return flow channels 38 are displaced such that the unlocking piston 15 can be pressurized with the fluid.
  • the fluid to be removed from the piston chamber 50 during the retracting movement of the piston rod 8 flows via the further line 49 through the check valve 43.2, the annular chamber 44 and the bore 45.2 into the oil-returning blocking tube 42 and further via the oil-returning valve with valve chamber 35, line 34 , the outer ring channel 33, the lower connecting line 32 to the drain connection 30.
  • State 2 - the unlocked system is to be locked immediately when the piston rod 8 retracts due to a sudden drop in the pressure of the fluid, for example an accident in the pressure line, in order to prevent the lowering of the external load.
  • the size of the force of the locking spring 13 is dimensioned such that the return torque introduced as a result of the action of an external load on the piston rod 8 via the rotating threaded spindle 9 is held against rotation. Leakage oil from the displacement 14 and the area of the locking spring 13 are discharged into the piston space 50 in a known manner via the check valve 20 with each stroke of the unlocking piston 15.
  • the threaded spindle 9 is received, as is technically customary, by a plain bearing and held by means of a thrust washer and a locking ring.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Optical Record Carriers And Manufacture Thereof (AREA)
  • Pens And Brushes (AREA)
  • Mutual Connection Of Rods And Tubes (AREA)
  • Vehicle Body Suspensions (AREA)
EP01114451A 2000-07-06 2001-06-15 Vérin à fluide sous pression avec verrouillage mécanique lorsque non pressurisé Expired - Lifetime EP1170512B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE20011789U 2000-07-06
DE20011789U DE20011789U1 (de) 2000-07-06 2000-07-06 Druckmittelbetriebener Arbeitszylinder mit mechanischer Wegsperrung im drucklosen Zustand

Publications (2)

Publication Number Publication Date
EP1170512A1 true EP1170512A1 (fr) 2002-01-09
EP1170512B1 EP1170512B1 (fr) 2004-01-21

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EP01114451A Expired - Lifetime EP1170512B1 (fr) 2000-07-06 2001-06-15 Vérin à fluide sous pression avec verrouillage mécanique lorsque non pressurisé

Country Status (3)

Country Link
EP (1) EP1170512B1 (fr)
AT (1) ATE258275T1 (fr)
DE (2) DE20011789U1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1420171A2 (fr) * 2002-10-22 2004-05-19 Bümach Engineering International B.V. Vérin hydraulique
EP1605171A2 (fr) 2004-06-11 2005-12-14 Bümach Engineering International B.V. Vérin à fluide sous pression avec bloquage mécanique
EP1803943A2 (fr) 2005-12-29 2007-07-04 Bümach Engineering International B.V. Vérin avec verrouillage de position mécanique en cas d'absence de pression

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITTO20011066A1 (it) * 2001-11-13 2002-02-13 Rolfo Spa Attuatore lineare con bloccaggio meccanico interno.
DE102004022203B3 (de) * 2004-05-05 2005-08-11 Neumeister Hydraulik Gmbh Verriegelungszylinder mit Gewinde-Freilauf
DE102006030617B4 (de) * 2005-12-29 2009-09-10 Bümach Engineering International B.V. Druckmittelbetriebener Arbeitszylinder mit mechanischer Wegsperrung im drucklosen Zustand

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB683633A (en) * 1949-02-25 1952-12-03 Gen Motors Corp Improved fluid-pressure actuator
GB725003A (en) * 1952-03-27 1955-03-02 Gen Motors Corp Improved fluid-pressure actuator
EP0648942A1 (fr) * 1993-10-06 1995-04-19 UNIVER S.p.A. Dispositif linéaire de manoeuvre pneumatique avec un mécanisme de blocage réversible
JPH08303410A (ja) * 1995-04-27 1996-11-19 Hino Motors Ltd 流体圧シリンダ
DE29720838U1 (de) * 1997-11-25 1998-02-26 Andexser, Lucie, 32584 Löhne Arbeitszylinder mit integrierter Hubbremse
EP1106841A2 (fr) * 1999-12-07 2001-06-13 Weber-Hydraulik GmbH Actionneur de positionnement linéaire

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2804053A (en) * 1954-04-14 1957-08-27 Gen Motors Corp Actuator and locking means therefor
US2879746A (en) * 1955-12-08 1959-03-31 Gen Motors Corp Actuator with unidirectional locking means
US3442176A (en) * 1967-05-01 1969-05-06 Gen Electric Actuator locking mechanism

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB683633A (en) * 1949-02-25 1952-12-03 Gen Motors Corp Improved fluid-pressure actuator
GB725003A (en) * 1952-03-27 1955-03-02 Gen Motors Corp Improved fluid-pressure actuator
EP0648942A1 (fr) * 1993-10-06 1995-04-19 UNIVER S.p.A. Dispositif linéaire de manoeuvre pneumatique avec un mécanisme de blocage réversible
JPH08303410A (ja) * 1995-04-27 1996-11-19 Hino Motors Ltd 流体圧シリンダ
DE29720838U1 (de) * 1997-11-25 1998-02-26 Andexser, Lucie, 32584 Löhne Arbeitszylinder mit integrierter Hubbremse
EP1106841A2 (fr) * 1999-12-07 2001-06-13 Weber-Hydraulik GmbH Actionneur de positionnement linéaire

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 1997, no. 03 31 March 1997 (1997-03-31) *

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1420171A2 (fr) * 2002-10-22 2004-05-19 Bümach Engineering International B.V. Vérin hydraulique
EP1420171A3 (fr) * 2002-10-22 2004-05-26 Bümach Engineering International B.V. Vérin hydraulique
EP1605171A2 (fr) 2004-06-11 2005-12-14 Bümach Engineering International B.V. Vérin à fluide sous pression avec bloquage mécanique
EP1605171A3 (fr) * 2004-06-11 2006-09-06 Bümach Engineering International B.V. Vérin à fluide sous pression avec bloquage mécanique
EP1803943A2 (fr) 2005-12-29 2007-07-04 Bümach Engineering International B.V. Vérin avec verrouillage de position mécanique en cas d'absence de pression
EP1803943A3 (fr) * 2005-12-29 2009-04-08 Bümach Engineering International B.V. Vérin avec verrouillage de position mécanique en cas d'absence de pression

Also Published As

Publication number Publication date
DE20011789U1 (de) 2000-12-21
DE50101349D1 (de) 2004-02-26
EP1170512B1 (fr) 2004-01-21
ATE258275T1 (de) 2004-02-15

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