EP1528267B1 - Dispositif de verrouillage - Google Patents

Dispositif de verrouillage Download PDF

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Publication number
EP1528267B1
EP1528267B1 EP04023895A EP04023895A EP1528267B1 EP 1528267 B1 EP1528267 B1 EP 1528267B1 EP 04023895 A EP04023895 A EP 04023895A EP 04023895 A EP04023895 A EP 04023895A EP 1528267 B1 EP1528267 B1 EP 1528267B1
Authority
EP
European Patent Office
Prior art keywords
outer ring
springs
rod
clamping
load
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.)
Active
Application number
EP04023895A
Other languages
German (de)
English (en)
Other versions
EP1528267A1 (fr
Inventor
Erich W. Dr. Schmalenbach
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.)
Sitema GmbH and Co KG
Original Assignee
Sitema GmbH and Co KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Sitema GmbH and Co KG filed Critical Sitema GmbH and Co KG
Publication of EP1528267A1 publication Critical patent/EP1528267A1/fr
Application granted granted Critical
Publication of EP1528267B1 publication Critical patent/EP1528267B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F15B15/262—Locking mechanisms using friction, e.g. brake pads

Definitions

  • the invention relates to a device for jamming a rod under load by means of at least one acting on the rod circumference clamping element, wherein the clamping element is conically shaped at its outer periphery and slidably guided in a corresponding conically shaped outer ring, such that the clamping element when driving through the rod is pressed in the load direction self-reinforcing against the rod, wherein the outer ring is guided axially displaceably in a housing and biased by springs.
  • clamping devices are used for example for fixing lifting tables, support cylinders, theater podiums and the like. Often they also act as fall protection for vertical axes of machine tools or handling equipment.
  • the clamping devices are hydraulically or pneumatically held in the open position and effective at pressure drop.
  • the energy of the sinking load is used to generate the clamping force.
  • a clamping device having the feature of the preamble of claim 1 has become known from EP-A 538 962. It is the jamming of a push rod in a motor vehicle steering, wherein a mechanical, dependent on the steering wheel position displacement movement is superimposed with a hydraulic displacement movement.
  • a similar clamping device is known from DE 38 11 225.
  • the clamping elements are taken in the case of release of the rod in the load direction, wherein the conical outer contour of the clamping elements generates a self-reinforcing static friction on the rod.
  • the clamping elements run - as far as the rated load is not significantly exceeded - not against a housing-fixed stop. Overloading can therefore lead to the destruction of the clamping device by plastic deformation. This feature limits the scope of use to those cases where overloads are excluded. Therefore, these clamping devices are not particularly suitable for dissipating the kinetic energy of a falling mass, they block the clamping bars, but are not suitable for braking.
  • the present invention has the object to develop a clamping device which allows an exact limitation of the holding force, wherein in the overload case targeted slippage of the rod occurs without damaging the clamping device, in particular without plastic deformation of the relevant parts.
  • the clamping device according to the invention should be characterized by low-cost and low tolerance-sensitive structure.
  • clamping element is loaded by spring elements in the clamping direction, and that the bias of acting on the outer ring springs against the load direction is directed and dimensioned so that the displacement of the outer ring only when a predetermined, defined load enters the pole.
  • this is a conical bush, which has one or more axial slots in its effective area. But it is also not excluded to work with several circumferentially juxtaposed clamping elements.
  • the outer ring surrounding the clamping elements is expediently designed as a closed ring, but could also consist of several parts, but care must be taken to intercept the radial forces occurring.
  • the clamping element runs only after exceeding the predetermined defined load axially against its stop, it is recommended that the bias of the outer ring engaging springs to select slightly higher than it would be required for holding the predetermined defined load (nominal load).
  • the spring travel of the responsible for the bias of the outer ring springs is chosen so that the axial displacement of the outer ring does not push the springs in their blocking position, but said springs should a defined force on the outer ring and thus a defined holding or braking force generate the rod when the axial displacement of the clamping element is completed.
  • the clamping element can run directly against the abovementioned stop. In terms of a compact design, it is recommended to interpose the responsible for the release of the clamping element release piston.
  • the outer ring surrounding the clamping elements not only in the unloaded state, but also under load axially spaced from the release piston or to the stop is arranged, whereas the clamping element is always held in contact with the release piston. The latter takes place in that it is loaded in the usual way by spring elements in the clamping direction.
  • the housing 1 is fixedly mounted in a manner not shown, while the rod 2 is the displaceable machine element to be held by the clamping device.
  • the rod 2 is surrounded by clamping elements, which in the embodiment have the shape of a conical sleeve 3 on its outer periphery.
  • This conical bush has axial slots in a known manner, so that it is elastic in the radial direction. It is in the inner cone of an outer ring 4, which will be discussed in more detail later and is loaded in the axial direction by a cup spring package 5 in the clamping direction.
  • the clamping bush 3 At its end facing away from the spring assembly 5, the clamping bush 3 abuts against a release piston 6, which in turn is axially displaceably guided in the housing part 1 b.
  • the release piston 6 At its end facing away from the clamping bush 3, the release piston 6 forms a cylinder space 7 with the housing part 1 b.
  • This cylinder space 7 can be acted upon by a housing bore with pressure medium - compressed air or hydraulic oil. so that he can move the clamping sleeve 3 from its clamping position to the left.
  • the stroke of the release piston 6 is limited in the release position by a stop ring 8.
  • This stop ring is suitably seated in a recess at the transition between the two housing halves 1 a and 1 b and is thus fixed axially.
  • outer ring 4 is axially slidably guided in the housing part 1a and that it is biased by springs 9 - preferably a disc spring package - against the load direction, ie in the sense of jamming of the clamping bush 3.
  • the disc springs 9 are arranged in an annular recess of the outer ring 4 and are based on their outer ring facing away from the end face on the abovementioned stop ring 8.
  • the bias of the disc springs 9 is selected so that they yield only when a load occurs in the rod 2, which is above the rated load of the clamping device. This results in the following function:
  • the rod 2 should be able to pass the clamping device in both directions.
  • the cylinder chamber 7 is acted upon with pressure medium, so that the release piston 6 moves the clamping cone 3 against the spring elements acting on it 5 to the left in the release position and holds there. This condition is shown in FIG.
  • the clamping state is triggered by the fact that the pressure in the cylinder chamber 7 is turned off. This allows the springs 5 to move the cone ring to the right, this displacement movement is supported by the movement of the rod 2 and brings about the known self-locking jamming.
  • FIG. 4 shows the associated force / displacement diagram.
  • the disc springs 9 Upon reaching the rated load or shortly thereafter, the disc springs 9 come into effect. Therefore, here the characteristic curves in a flat area, namely until the clamping bush 3 abuts on the release piston 6 on the housing 1, as shown in Figure 3. With further increase in load, the holding force of the clamping device is finally exceeded and it comes to slippage, wherein the holding or braking force is defined by the strength of the disc springs 9.
  • the braking force is inventively greater than the weight of the moving mass, therefore, an effective braking of the mass is guaranteed.
  • the invention thus offers the advantage that, while maintaining the conventional manufacturing tolerances, it is possible to specify a precisely defined limitation of the clamping force, above which targeted slipping of the rod is permitted.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Clamps And Clips (AREA)
  • Lock And Its Accessories (AREA)
  • Actuator (AREA)

Claims (8)

  1. Dispositif pour serrer une tige (2) placée sous charge au moyen d'au moins un élément de serrage (3) agissant sur le pourtour de la tige, l'élément de serrage (3) ayant une forme conique sur son pourtour extérieur et étant guidé de manière déplaçable dans une bague extérieure (4) ayant une forme conique correspondante, de telle façon que l'élément de serrage (3) soit pressé, en direction de la charge, contre la tige (2) en assurant son propre renforcement lorsqu'il est entraîné par la tige (2), la bague extérieure (4) étant guidée de manière déplaçable axialement dans un boîtier (1) et étant mise en précontrainte par des ressorts (9), caractérisé en ce que l'élément de serrage (3) est mis en charge, en direction de serrage, par des éléments de ressorts (5) et en ce que la précontrainte produite par les ressorts (9) agissant sur la bague extérieure (4) est orientée dans le sens opposé à la direction de la charge et est dimensionnée de telle façon que le déplacement de la bague extérieure (4) ne se produise que si une charge prescrite et définie agissant sur la tige (2) est dépassée.
  2. Dispositif selon la revendication 1,
    caractérisé en ce
    que le débattement théorique des ressorts (9) qui réalisent la précontrainte est plus grand que le déplacement axial maximum de la bague extérieure (4) lorsqu'elle est sous charge.
  3. Dispositif selon la revendication 1,
    caractérisé en ce
    que - de préférence lorsqu'au moins un piston de desserrage (6) est interposé - l'élément de serrage (3) se déplace, en direction de la charge, contre une butée se trouvant dans le boîtier (1).
  4. Dispositif selon la revendication 3,
    caractérisé en ce
    que - lorsqu'elle est sous charge - la bague extérieure (4) est disposée avec un espacement axial par rapport au piston de desserrage (6).
  5. Dispositif selon la revendication 3,
    caractérisé en ce
    que l'élément de serrage (3) est en contact axial avec le piston de desserrage (6).
  6. Dispositif selon la revendication 1,
    caractérisé en ce
    que la force des ressorts (9) qui assurent la précontrainte de la bague extérieure (4) est plus importante de la valeur d'un multiple que celle des éléments de ressorts (5) agissant sur la douille de serrage (3).
  7. Dispositif selon la revendication 1,
    caractérisé en ce
    que les ressorts (9) qui assurent la précontrainte de la bague extérieure (4) sont dimensionnés de telle façon que la force de maintien qu'ils génèrent est plus importante que la charge maximale agissant sur la tige (2).
  8. Dispositif selon la revendication 1,
    caractérisé en ce
    que les ressorts (9) qui assurent la précontrainte s'appuient sur une bague de butée fixe (8) qui limite en même temps le trajet d'ajustement du piston de desserrage (6) dans la position de desserrage.
EP04023895A 2003-10-27 2004-10-07 Dispositif de verrouillage Active EP1528267B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10350225 2003-10-27
DE10350225A DE10350225A1 (de) 2003-10-27 2003-10-27 Feststellvorrichtung

Publications (2)

Publication Number Publication Date
EP1528267A1 EP1528267A1 (fr) 2005-05-04
EP1528267B1 true EP1528267B1 (fr) 2007-01-24

Family

ID=34399573

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04023895A Active EP1528267B1 (fr) 2003-10-27 2004-10-07 Dispositif de verrouillage

Country Status (6)

Country Link
US (1) US7178639B2 (fr)
EP (1) EP1528267B1 (fr)
JP (1) JP2005132632A (fr)
AT (1) ATE352721T1 (fr)
CA (1) CA2485613A1 (fr)
DE (2) DE10350225A1 (fr)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005052755B4 (de) * 2005-06-14 2014-11-20 Bosch Rexroth Aktiengesellschaft Hydraulisch betätigte Klemmeinheit und damit ausgeführte hydraulische Regelachse
DE102006004659A1 (de) * 2006-01-31 2007-08-02 Sitema Gmbh & Co. Kg Klemmvorrichtung
US20070246785A1 (en) * 2006-04-20 2007-10-25 Asml Netherlands B.V. Locking device, adjustment mechanism and lithographic apparatus
US8020893B2 (en) * 2007-09-27 2011-09-20 Caterpillar Inc. Steering column assembly including a mechanical strut and machine using same
US7748785B2 (en) * 2007-09-27 2010-07-06 Caterpillar Inc Seat assembly including a mechanical strut and machine using same
DE102009011003A1 (de) * 2009-03-02 2010-09-09 Sitema Gmbh & Co. Kg Klemmeinheit, insbesondere zur Verwendung als Formschließeinheit
DE102010023699B4 (de) 2010-06-14 2012-02-23 Pintsch Bubenzer Gmbh Selbstverstärkende Bremseinrichtung
DE102010023701A1 (de) 2010-06-14 2011-12-15 Pintsch Bubenzer Gmbh Lüftgerät für eine Bremseinrichtung
DE102010023700B4 (de) * 2010-06-14 2012-01-26 Pintsch Bubenzer Gmbh Stellvorrichtung für eine selbstverstärkende Bremseinrichtung und selbstverstärkende Bremseinrichtung
CN102425586B (zh) * 2011-12-21 2014-12-10 徐州重型机械有限公司 一种液压油缸、液压***及工程机械
CN102628463A (zh) * 2012-04-03 2012-08-08 无锡亿利大机械有限公司 机械自锁液压缸
CN103362896B (zh) * 2013-07-23 2016-08-24 云南兴长江实业有限公司 一种适合于液压油缸的安全锁定装置
KR101512471B1 (ko) * 2014-09-11 2015-04-16 한국뉴매틱(주) 록-블록을 이용한 로드부재 록킹장치
DE102015212851A1 (de) * 2015-07-09 2017-01-12 Sms Group Gmbh Hydraulikzylinder, Vorrichtung zum Umformen von Werkstücken, Verwendung eines stirnseitigen Deckelteils
US10040152B2 (en) * 2015-08-17 2018-08-07 GM Global Technology Operations LLC Mechanical lock for a work support
FI127824B (fi) * 2018-01-22 2019-03-15 Valmet Technologies Oy Massavaimennin ja järjestely kuiturainakoneessa
CN110513377A (zh) * 2019-09-19 2019-11-29 中国科学院武汉岩土力学研究所 锁紧装置和冲击设备

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Publication number Priority date Publication date Assignee Title
US2632425A (en) * 1950-05-26 1953-03-24 Reginald L Grover Piston lock
DE1804857B2 (de) * 1968-10-24 1971-11-25 Hänchen, Siegfried, 7304 Ruit Vorrichtung zur klemmung einer axial verschiebbaren kolben stange
DE2845266C2 (de) * 1978-10-18 1983-03-03 Ringspann Albrecht Maurer Kg, 6380 Bad Homburg Sicherheitsfeststellbremse für hydraulische Aufzüge, Hebebühnen u.dgl.
DE3118449A1 (de) * 1981-05-09 1982-12-02 Sitema Gesellschaft für Sicherheitstechnik und Maschinenbau mbH, 7500 Karlsruhe "klemmvorrichtung"
SE441468B (sv) * 1982-08-20 1985-10-07 Atlas Copco Ab Losbar lasningsanordning for en tryckmediemanovrerad kolvcylinder
DE3707046A1 (de) * 1987-03-05 1988-09-15 Haenchen Kg Herbert Klemmvorrichtung fuer stangen
DE3811225C2 (de) * 1988-04-02 1996-07-11 Sitema Hydraulische Stützvorrichtung für Fahrzeuge
DE8804418U1 (de) * 1988-04-02 1988-05-19 Sitema Gesellschaft für Sicherheitstechnik und Maschinenbau mbH, 7500 Karlsruhe Brems- und Feststellvorrichtung
DE3907780A1 (de) * 1989-03-10 1990-09-13 Bosch Gmbh Robert Bremseinrichtung fuer eine kolbenstange
DE4126897A1 (de) * 1991-08-14 1993-02-18 Rexroth Mannesmann Gmbh Hydraulisches klemmsystem
FR2682925B1 (fr) 1991-10-25 1997-08-29 Renault Dispositif de braquage des roues directrices d'un vehicule.
DE19508175A1 (de) * 1995-03-09 1996-09-12 Montan Hydraulik Gmbh & Co Kg Klemmvorrichtung für zylindrische, in achsialer Richtung verlagerbare oder drehende Teile
JP3856934B2 (ja) * 1998-01-27 2006-12-13 Ｓｍｃ株式会社 ロック機構付き流体圧シリンダ
US6367591B1 (en) * 1999-12-21 2002-04-09 Caterpillar Inc. Automatic brake clearance adjuster

Also Published As

Publication number Publication date
ATE352721T1 (de) 2007-02-15
US7178639B2 (en) 2007-02-20
EP1528267A1 (fr) 2005-05-04
CA2485613A1 (fr) 2005-04-27
DE502004002749D1 (de) 2007-03-15
JP2005132632A (ja) 2005-05-26
DE10350225A1 (de) 2005-05-19
US20050087405A1 (en) 2005-04-28

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