EP0949422B1 - Dispositif amortisseur de fin de course - Google Patents

Dispositif amortisseur de fin de course Download PDF

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Publication number
EP0949422B1
EP0949422B1 EP98123678A EP98123678A EP0949422B1 EP 0949422 B1 EP0949422 B1 EP 0949422B1 EP 98123678 A EP98123678 A EP 98123678A EP 98123678 A EP98123678 A EP 98123678A EP 0949422 B1 EP0949422 B1 EP 0949422B1
Authority
EP
European Patent Office
Prior art keywords
damping
piston
pressure medium
piston ring
end position
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.)
Expired - Lifetime
Application number
EP98123678A
Other languages
German (de)
English (en)
Other versions
EP0949422A1 (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
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 Buemach Engineering International BV filed Critical Buemach Engineering International BV
Publication of EP0949422A1 publication Critical patent/EP0949422A1/fr
Application granted granted Critical
Publication of EP0949422B1 publication Critical patent/EP0949422B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F15B15/224—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having a piston which closes off fluid outlets in the cylinder bore by its own movement

Definitions

  • the invention relates to an end position damping of a pressure medium-operated device, in particular a pneumatic or hydraulic working cylinder.
  • IPC International Patent Classification
  • fluid operated devices are classified in the IPC F15B15 / 00, details of the delay in stroke are recorded in the IPC F15B15 / 22.
  • the pressure medium itself can delay or dampen the stroke of a piston in a cylinder.
  • the damping force which is preferably proportional to the speed of movement of the piston, is achieved via a corresponding counterpressure on the piston.
  • a throttled pressure medium flow offers itself as a passive variant, in which the pressure medium crosses a throttle. There is approximately a proportional relationship between the pressure medium volume flowing through the throttle and the pressure difference on both sides of the throttle.
  • the proportionality factor as a characteristic value is essentially determined by the geometry of the throttle.
  • the desired throttling should only take effect when the end position is approached. Accordingly, the flow state must change depending on the position of the piston in the cylinder, in particular with regard to the end position. This can be achieved through various measures.
  • damping space which is arranged behind the actual outlet opening with respect to the direction of movement of the piston.
  • the pressure medium located in this damping space can only escape throttled into the actual outlet opening when the piston is immersed in this damping space.
  • the throttle itself is formed by the annular gap between the piston and the cylinder and remains constant in its characteristic value with regard to the immersion depth.
  • a solution previously known from US4425836 uses a helical recess on the outer surface of the piston as a throttle. Due to the piston position in the damping chamber, the effective length of the throttle geometry determining the characteristic value changes accordingly, whereby this increases linearly with the depth of penetration.
  • a disadvantage is the compulsory linear increase in the characteristic value, unless one realizes complex helical structures with a variable gradient value and / or cross section.
  • an extension-side end position brake for hydraulic or pneumatic working cylinders with disc pistons based on the principle of path-dependent throttling of the escaping fluid by means of an orifice which consists of an annular throttle orifice blasted at one point with axial grooves on the inner jacket with a continuation exists on the flat surface facing the piston and sits in a groove of the piston rod.
  • the throttle disc is immersed in a bushing and throttles the cross-section for the exit of the fluid depending on the path through correspondingly ground axial grooves in the inner jacket of the bushing, the fluid flowing through these grooves and the axial gap between the piston rod and throttle orifice.
  • the disadvantages of this solution are, in particular, the throttle disk, which is very complex to manufacture, and the weakening of the piston rod by the groove for receiving the throttle disk.
  • the object of the invention is to develop an end position damping device of the type described above, with a structurally simple solution making it possible to implement any desired characteristic curve of the throttle with respect to the immersion depth and to change this curve easily.
  • the invention consists in the use of the existing gap of a piston ring as a throttle element and the change in its effective opening as a function of the immersion depth via the change in the cylinder inner diameter predetermined by a special bushing.
  • the piston ring has the smallest outflow cross-section when it is guided inside the cylinder tube or when it is in the end position of the damping bush.
  • the taper of the damping bush is only so great that the end face of the same is gripped by the end face of the cylinder tube, so that when the locking parts are tightened, the damping bushing or in the case of use in the differential working cylinder, the bushings are firmly clamped.
  • the entrained piston ring jumps open radially in the area of the largest diameter of the damping bush due to its internal internal stress and blocks the radial bores provided for the outflow, as a result of which the outflow described above is forced.
  • the piston ring gap is closed down to the smallest outflow cross section. Due to the radial flexibility of the piston ring and the taper of the damping bush, this moving infeed of the discharge cross-section is achieved.
  • the damping is progressive depending on the cone angle of the damping bush.
  • the interchangeability of the piston ring and the conical damping bush enables the damping characteristics to be changed in a simple manner, which makes it possible to easily take special requirements into account in the application.
  • the length of the cone of the damping bush determines the length of the damping path.
  • the damping path itself is part of the overall stroke.
  • Fig. 1 shows in connection with the detail according to Fig. 2, the detail piston ring according to Fig. 3 and the detail damping bushing according to Fig. 4, a differential working cylinder which is provided in the stroke end positions with damping bushings 1, which as part of the stroke 2, the Guide piston 3 in the end position area.
  • the piston 3 separates the working chamber of the differential working cylinder into the parts piston chamber 5.1 and annular piston chamber 5.2 by sealing by means of a piston seal 4.
  • the piston 3 is provided with piston rings 6, which are held in grooves 7 of the piston 3, the residual stress behavior of which enables them to expand slightly beyond the piston diameter. For this reason, the piston ring 6 is selected such that it has the smallest gap width 8 when it is guided in the cylinder tube 9.
  • the piston 3 is expanded radially as a result of its residual stress behavior to a maximum inner cone diameter 11 of the damping bush 1 as the movement continues.
  • the piston ring 6 is therefore always larger than the largest cone inner diameter 11 in the relaxed state, in order to lie securely on all the inner diameters along the stroke 2.
  • radial bores 12 are provided which guide the pressure medium in longitudinal grooves 13, where it reaches the drain connection 15 via an annular channel 14.
  • Crossing the piston ring 6 becomes the position of the radial bores 12 the amount of pressure medium located in front of the piston 3 is only discharged via the gap width 8 of the piston ring 6, as a result of which the damping sets in, which results in the progress of the movement of the piston 3 towards the end positions as a result of the effect of an inner cone 16 as damping with a progressive character.
  • the throttled pressure medium flowing out over the gap width 8 passes through the radial bores 12 and longitudinal grooves 13 into the annular channel 14 and in this way to the drain connection 15 Mistake.
  • the damping bushing 1 is clamped by screwing via a thread 19, an end face 20 of the cylinder tube 9 pressing against a damping bushing end face 21 and the same with an outer end face 22 against an inner face 23 of the closure part 17.1.
  • the low roughness of these surfaces ensures that the pressure medium flow does not reach the drain connection 15 in this way in order to obtain the necessary back pressure in the annular piston chamber 5.2.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Damping Devices (AREA)
  • Actuator (AREA)
  • Golf Clubs (AREA)
  • Superconductors And Manufacturing Methods Therefor (AREA)
  • Memory System Of A Hierarchy Structure (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Claims (3)

  1. Amortisseur de fin de course d'un dispositif entraîné par un agent sous pression, dans lequel la course (2) d'un piston (3) dans un cylindre (9) est ralentie en engendrant une contre-pression à l'intérieur de la zone d'amortissement (10), par étranglement de l'agent de pression refoulé avant qu'il ne s'échappe à travers des canaux reliés au raccord de sortie (15), l'étranglement étant produit par une bague (6) montée dans une gorge (7) du piston (3),
    caractérisé en ce que
    - le cylindre (9), au niveau des fins de course, est équipé de douilles d'amortissement (1) qui assurent le guidage du piston (3) dans les zones de fin de course,
    - la bague de piston (6) a un comportement propre sous tension qui lui permet de s'expanser au-delà du diamètre du piston et de ce fait d'atteindre radialement un plus grand diamètre (11) interne d'un cône,
    - un cône intérieur (16) de la douille d'amortissement (1) assure un amortissement à caractère progressif,
    - la largeur (8) de la fente de la bague de piston (6) atteint sa valeur la plus faible quand la bague 'est à l'intérieur du tube (9) du cylindre,
    dans la zone de la douille d'amortissement (1) il est prévu des perçages radiaux (12) qui amènent l'agent de pression dans des rainures longitudinales (13) et de là, par un canal circulaire (14) au raccord de sortie (15).
  2. Amortisseur de fin de course selon la revendication 1,
    caractérisé en ce que
    l'agent de pression dont l'écoulement est étranglé par la largeur de la fente (8) passe ensuite à travers les perçages radiaux (12) et les rainures longitudinales (13) dans le canal annulaire (14) et de cette manière parvient au raccord de sortie (15).
  3. Amortisseur de fin de course selon la revendication 1 ou 2,
    caractérisé en ce que
    - la douille d'amortissement (1) est serrée par vissage sur un filetage (19), une face frontale (20) du tube de cylindre (9) étant en pression contre une face frontale (21) d'une double d'amortissement qui est elle-même en pression par une face frontale externe (22) sur une portée interne (23) de la pièce de fermeture (17, 1), et
    - la faible profondeur de rugosité des portées (20, 21, 22, 23) est telle que le courant de l'agent de pression n'emprunte pas ce chemin pour gagner le raccord de sortie (15).
EP98123678A 1998-03-04 1998-12-11 Dispositif amortisseur de fin de course Expired - Lifetime EP0949422B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE29803739U DE29803739U1 (de) 1998-03-04 1998-03-04 Endlagendämpfung
DE29803739U 1998-03-04

Publications (2)

Publication Number Publication Date
EP0949422A1 EP0949422A1 (fr) 1999-10-13
EP0949422B1 true EP0949422B1 (fr) 2001-09-19

Family

ID=8053522

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98123678A Expired - Lifetime EP0949422B1 (fr) 1998-03-04 1998-12-11 Dispositif amortisseur de fin de course

Country Status (5)

Country Link
US (1) US6047627A (fr)
EP (1) EP0949422B1 (fr)
JP (1) JP3026802B2 (fr)
AT (1) ATE205916T1 (fr)
DE (2) DE29803739U1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10214864C5 (de) * 2002-04-04 2009-12-17 Linde Material Handling Gmbh Hydraulischer Zylinder mit Endlagendämpfung
DE202009014682U1 (de) 2009-10-30 2010-01-07 Bümach Engineering International B.V. Endlagendämpfungsvorrichtung eines linearen Druckstromverbrauchers
DE102010024505A1 (de) 2010-06-21 2011-12-22 Pacoma Gmbh Endlagengedämpfter Druckmittelzylinder
DE102012217531A1 (de) 2012-09-27 2014-03-27 Jungheinrich Aktiengesellschaft Hydraulikzylinder mit unter Verwendung einer Spiralnut realisierter Ausfahrdämpfung
WO2021129900A1 (fr) 2019-12-23 2021-07-01 Bümach Engineering International B. V. Cylindre de travail à amortissement en position finale
DE202020004388U1 (de) 2020-10-19 2022-01-20 Bümach Engineering International B.V. Endlagengedämpfter Arbeitszylinder und Dämpfungskolbenring
DE202020004533U1 (de) 2020-10-28 2022-02-04 Bümach Engineering International B.V. Endlagengedämpfter Arbeitszylinder
WO2022083811A1 (fr) 2020-10-19 2022-04-28 Bümach Engineering International B.V. Cylindre de travail à amortissement de position finale, et segment de piston d'amortissement

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9910257D0 (en) * 1999-05-05 1999-06-30 Lucas Ind Plc Piston and cylinder assembly and flow restrictor device therefor
DE10105101C1 (de) * 2001-02-05 2002-12-12 Zf Sachs Ag Hydraulischer Zuganschlag für Schwingungsdämpfer
EP1998054B1 (fr) * 2007-05-24 2014-08-13 Parker Origa Holding AG Cylindre pneumatique avec amortissement à réglage automatique en position finale et procédé
JP3191509U (ja) * 2014-04-14 2014-06-26 Smc株式会社 流体圧シリンダ
JP6159938B2 (ja) * 2014-04-14 2017-07-12 Smc株式会社 流体圧シリンダ
CN114215818B (zh) * 2021-12-17 2023-10-31 张家港市友明机械制造有限公司 一种双头缓冲油压缸

Family Cites Families (11)

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Publication number Priority date Publication date Assignee Title
US2935051A (en) * 1958-05-28 1960-05-03 Curtiss Wright Corp Fluid operated reciprocating motors
DE1925166C3 (de) * 1969-05-14 1978-05-18 Siemens Ag, 1000 Berlin Und 8000 Muenchen Hydraulische Betätigungsvorrichtung für elektrische Hochspannungsschalter
DE6943765U (de) * 1969-11-07 1970-03-26 Montan Hydraulik Gmbh & Co Kg Hydraulikzylinder mit endlagendaempfung
DE2206410A1 (de) * 1972-02-11 1973-08-16 Erling Mangseth Vorrichtung zum daempfen der kolbenbewegung in einem hydraulischen zylinder
DD105493A1 (fr) * 1973-06-19 1974-04-20
FR2319795A1 (fr) * 1975-08-01 1977-02-25 Renault Dispositif d'acceleration en debut de course de verin hydraulique
US4048905A (en) * 1976-03-29 1977-09-20 The Boeing Company Variable orifice hydraulic snubber
US4207800A (en) * 1978-11-02 1980-06-17 Homuth Kenneth C Single directional sealing piston ring
US4296675A (en) * 1979-07-16 1981-10-27 Aeroquip Corporation Cylinder cushion with contractable ring
US4425836A (en) * 1981-02-20 1984-01-17 Government Innovators, Inc. Fluid pressure motor
DE4307265C1 (de) * 1993-03-02 1994-08-11 Mannesmann Ag Vorrichtung zur Endlagendämpfung eines Kolbens in Druckflüssigkeitszylindern

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10214864C5 (de) * 2002-04-04 2009-12-17 Linde Material Handling Gmbh Hydraulischer Zylinder mit Endlagendämpfung
DE202009014682U1 (de) 2009-10-30 2010-01-07 Bümach Engineering International B.V. Endlagendämpfungsvorrichtung eines linearen Druckstromverbrauchers
DE102010024505A1 (de) 2010-06-21 2011-12-22 Pacoma Gmbh Endlagengedämpfter Druckmittelzylinder
DE102012217531A1 (de) 2012-09-27 2014-03-27 Jungheinrich Aktiengesellschaft Hydraulikzylinder mit unter Verwendung einer Spiralnut realisierter Ausfahrdämpfung
WO2021129900A1 (fr) 2019-12-23 2021-07-01 Bümach Engineering International B. V. Cylindre de travail à amortissement en position finale
US11953033B2 (en) 2019-12-23 2024-04-09 Buemach Engineering International B.V. Working cylinder with cushioned end-stroke
DE202020004388U1 (de) 2020-10-19 2022-01-20 Bümach Engineering International B.V. Endlagengedämpfter Arbeitszylinder und Dämpfungskolbenring
WO2022083811A1 (fr) 2020-10-19 2022-04-28 Bümach Engineering International B.V. Cylindre de travail à amortissement de position finale, et segment de piston d'amortissement
DE202020004533U1 (de) 2020-10-28 2022-02-04 Bümach Engineering International B.V. Endlagengedämpfter Arbeitszylinder
EP3992469A1 (fr) 2020-10-28 2022-05-04 Bümach Engineering International B.V. Cylindre de travail amorti en fin de course

Also Published As

Publication number Publication date
JP3026802B2 (ja) 2000-03-27
JPH11294414A (ja) 1999-10-26
ATE205916T1 (de) 2001-10-15
US6047627A (en) 2000-04-11
DE59801513D1 (de) 2001-10-25
DE29803739U1 (de) 1998-05-28
EP0949422A1 (fr) 1999-10-13

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