EP1447571B1 - Cylindre à amortissement de fin de course réglable - Google Patents

Cylindre à amortissement de fin de course réglable Download PDF

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Publication number
EP1447571B1
EP1447571B1 EP20040100496 EP04100496A EP1447571B1 EP 1447571 B1 EP1447571 B1 EP 1447571B1 EP 20040100496 EP20040100496 EP 20040100496 EP 04100496 A EP04100496 A EP 04100496A EP 1447571 B1 EP1447571 B1 EP 1447571B1
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EP
European Patent Office
Prior art keywords
piston
travel
damping
pneumatic cylinder
stop element
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
EP20040100496
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German (de)
English (en)
Other versions
EP1447571A1 (fr
Inventor
Ernst-August Meyer
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.)
Aventics GmbH
Original Assignee
Rexroth Mecman GmbH
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Publication date
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Application filed by Rexroth Mecman GmbH filed Critical Rexroth Mecman GmbH
Publication of EP1447571A1 publication Critical patent/EP1447571A1/fr
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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
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F15B15/223—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having a piston with a piston extension or piston recess which completely seals the main fluid outlet as the piston approaches its end position

Definitions

  • the invention relates to an endlagengedämpften pneumatic cylinder, in whose Cylinder housing an at least one side acted upon piston axially movable is accommodated, wherein at least one of the two pressure chambers formed thereby Means is equipped for an adjustable end position damping of the piston.
  • damping is the speed of the piston shortly before reaching the end position by braked corresponding components, which usually form an additional throttle point in principle, through which the compressed air to be displaced from the pneumatic cylinder flow must, so that the desired delay arises.
  • From DE 196 45 701 A1 is another generic endlagegedämpfter Pneumatic cylinder with variable damping length out.
  • the damping is here by means of a control valve arrangement generates, through which the compressed air flowing through at least is temporarily throttled.
  • the control valve assembly has compressed air connections and Control terminals connected to an electronic control unit.
  • Throttling of the compressed air flow has the control valve arrangement in addition to a first Passage cross section still a second, smaller passage cross-section and a Change-over valve for switching between the two passage cross-sections.
  • the Switching to the smaller passage cross-section is a temporary throttling of the Compressed air supply in the pressure cylinder for cushioning causes.
  • About the electronic control unit is because of a cooperating with this permanent Position detection of the piston the onset of cushioning, that is the here Switching between the two passage cross sections, flexibly adjustable. Indeed This solution requires a fairly high amount of additional valve technology as well Control electronics.
  • the invention includes the technical teaching that as a means for an adjustable End position damping a frontally spaced on the piston via compression spring means attached, at least partially iron metallic stop element is provided, which in a piston near basic position G by the magnetic force of at least one Permanent magnet is fixed to the piston, and which in a piston remote working position A protrudes into the adjacent pressure chamber for cushioning, with an outside along the cylinder housing for determining the damping length adjustable Magnetic element for the generation of a relative to the magnetic field of the permanent magnet is provided in substantially inverted magnetic field to a change in position of the To achieve stop element from the basic position G in the working position A, when the Piston passes shortly before reaching the end position of the magnetic element.
  • the advantage of the solution according to the invention lies in the fact that with a Adjustment of the outside of the cylinder housing attached magnetic element Damping length is flexibly adaptable to every application. This adjustment takes place in easy way manually, without the need for control engineering effort is required.
  • the damping strength can also be adjusted manually via an adjustable throttle in conventional Be customized.
  • the two are the end position damping Parameter damping length and damping strength directly on the pneumatic cylinder by light understandable operating steps adjustable.
  • the inventive mechanical solution for End position damping requires only a small additional component cost, the Compactness of the pneumatic cylinder is not affected. This is how the length of the Pneumatic cylinder thereby not increased.
  • a particularly reliable holding the iron metal stop member in the piston-close basic position G results when the permanent magnet is a hollow cylinder is formed, adapted to a preferably annular formation of the stop element, wherein the pressure spring means carrying the stop element from the hollow cylindrical Permanent magnet is at least partially enclosed.
  • This relative arrangement of said components to each other also ensures their compact Housing within the limited space in the piston.
  • the compression spring means in the manner of a coil spring or in the manner of a Elastomer bellows formed, which is attached on the one hand to the piston and on the other carries the stop element. It is conceivable that the compression spring itself by his Spring effect contributes to cushioning.
  • the compression spring means only a small specific spring constant, which is such that a Axial movement of the stop element of the piston near basic position G springing in the piston-distant working position A is ensured.
  • the cushioning is preferably such that the stop element in the far away from working position A when approaching the piston to the end position from reaching one defined by the axial spacing of the stop element from the piston Damping distance X a arranged in the associated cylinder cover corresponding Closes opening, so that for the rest of the pressure chamber escaping exhaust air only the residual flow cross-section provided by a second bypass opening remains.
  • the stop element advantageously consists of different Materials, namely to the piston side facing iron and to the opposite, the cylinder cover facing side of an elastomeric material.
  • the stop element can thus be produced in a simple manner as a rubber-metal part become.
  • the preferably annular stop element corresponds to the in Cylinder cover provided opening, which, for example, as an annular gap or as an in a circular array arranged hole series can be formed.
  • this is along the cylinder housing for determining the damping length adjustable magnetic element an electric solenoid, which is opposite to that in the piston integrated permanent magnet is aligned so that when energized opposite to the magnetic field of the permanent magnet substantially inverted magnetic field results, which disturbs the magnetic field of the permanent magnet by this partially will be annulled.
  • the energization of the solenoid can via an electronic Control unit, which is an optional switching on or off the End position damping allows.
  • the control of the solenoid can together with the control of a solenoid valve acting on the solenoid valve, so that a separate control device is not required.
  • the figure shows a longitudinal section through an endlagengedämpften pneumatic cylinder with variable damping length.
  • the pneumatic cylinder consists essentially of a cylinder housing 1, in which a piston 2 is housed axially displaceable.
  • the piston 2 is provided with two annular Sealing elements 3a and 3b provided, which on the inner wall of the cylinder housing. 1 come into contact via corresponding sealing lip sections.
  • the piston 2 divides the Interior of the cylinder housing 1 in two pressure chambers 4a and 4b.
  • the pressure chambers 4a and 4b are further limited by sealingly attached to the cylinder housing 1 at the end Cylinder cover 5a and 5b.
  • a piston rod 6 runs.
  • the piston rod 6 penetrates sealed by the cylinder cover 5b.
  • For sealing the cylinder cover 5b opposite the piston rod 6 is an annular sealing element 7 in the cylinder cover 5b arranged. Axially adjacent to the sealing element 7, the cylinder cover 5b continues to have a Guide bush 8, which serves a precise axial guidance of the piston rod 6.
  • two pressure medium connections 9a and 9b are provided in the cylinder cover 5a and 5b, respectively.
  • the pressure medium connection 9a is in communication with the pressure chamber 4a, whereas the Pressure medium connection 9b for acting on the pressure chamber 4b is used.
  • annular stop elements 10a, 10b correspond to the execution of the End position damping with associated openings 12a and 12b, which here take the form of a Have annular gaps, the shape of the acting as a closure element stop element 10a or 10b is adjusted.
  • the stop element 10a, 10b to the opening 12a or 12b facing side of an elastomeric material, whereas the opposite side is made of iron.
  • An adjustable end position damping is achieved in that the stop element 10a, 10b both a piston-near basic position G and a piston-distant working position A. can take. (In the figure, both positions are shown, which are equally for both damping sides apply.)
  • the piston-near basic position G is the iron-metallic Stop element 10b by the magnetic force of a hollow cylindrical permanent magnet 15a, 15b fixed to the piston 2.
  • piston-distant working position A stands out Stop element 10a - in the manner described above - in the adjacent Pressure chamber 4a into it.
  • a magnetic element 16a, 16b manually adjustable along the cylinder housing 1 and releasably secured thereto arranged.
  • the magnetic elements 16a, 16b are designed here as electrical magnetic coils, which are powered by a - not shown - electronic control unit. When the magnetic elements 16a and 16b are energized, they develop a magnetic field which is in its polarization with respect to the magnetic field generated by the permanent magnet 15a, 15b is inverted. By this disturbing weakening of the magnetic field of the permanent magnet 15a or 15b dissolves due to the pressing force of the Druckededemlittel 11a and 11b the Stop element 10a or 10b from its magnetic force held near the piston Basic position G and gets into its working position A. Now is the stop element 10a and 10b ready to perform a damping function in the sense explained above.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)

Claims (10)

  1. Cylindre pneumatique à amortissement de fin de course, comprenant un boítier de cylindre (1) dans lequel est logé un piston (2) sollicité sur au moins un côté et capable de translation axiale, dans lequel l'une au moins des deux chambres à pression (4a, 4b) ainsi formées est équipée de moyens pour assurer un amortissement de fin de course réglable du piston (2),
    caractérisé en ce qu'il est prévu, à titre de moyens pour assurer un amortissement de fin de course réglable, un élément de butée (10a, 10b) réalisé au moins localement en métal à base de fer et monté du côté frontal sur le piston (2) en étant gardé à distance par des moyens formant ressort de compression (11a, 11b), ledit élément de butée étant fixé sur le piston (2) dans une position de base G proche du piston grâce à la force magnétique d'au moins un aimant permanent (15a, 15b) et pénétrant dans la chambre à pression voisine (4a, 4b) dans une position de travail A éloignée du piston en vue de l'amortissement de fin de course, et en ce qu'il est prévu un élément magnétique (16a, 16b) déplaçable à l'extérieur le long du boítier de cylindre (1) pour déterminer la longueur d'amortissement et destiné à générer un champ magnétique sensiblement inversé par rapport au champ magnétique de l'aimant permanent (15a, 15b), afin d'atteindre une modification de position de l'élément de butée (10a, 10b) depuis la position de base G jusque dans la position de travail A, lorsque le piston (2) passe devant l'élément magnétique (16a, 16b) avant d'atteindre la position de fin de course.
  2. Cylindre pneumatique à amortissement de fin de course selon la revendication 1, caractérisé en ce que l'aimant permanent (15a, 15b) est réalisé sous forme de cylindre creux, et est encastré du côté frontal dans le piston (2) en entourant au moins partiellement les moyens formant ressort de compression (11a, 11b).
  3. Cylindre pneumatique à amortissement de fin de course selon l'une ou l'autre des revendications 1 et 2, caractérisé en ce que les moyens formant ressort de compression (11a, 11b) sont réalisés à la manière d'un ressort de compression spiralé ou à la manière d'un soufflet plissé en élastomère qui est fixé d'une part au piston (2) et qui porte d'autre part l'élément de butée (10a, 10b).
  4. Cylindre pneumatique à amortissement de fin de course selon l'une des revendications précédentes, caractérisé en ce que l'élément de butée (10a, 10b) referme une ouverture correspondante (12a ou 12b) ménagée dans le couvercle de cylindre (5a, 5b) associé, dans la position de travail A éloignée du piston, lors du rapprochement du piston (2) vers la position de fin de course à partir du moment où il a atteint une distance d'amortissement (X) définie par l'écartement axial de l'élément de butée (10a, 10b) depuis le piston (2), de sorte que pour l'air restant qui s'échappe hors de la chambre à pression (4a ou 4b), il ne reste plus qu'une section d'écoulement résiduelle mise à disposition par une seconde ouverture de by-pass (13a, 13b).
  5. Cylindre pneumatique à amortissement de fin de course selon l'une des revendications précédentes, caractérisé en ce que l'élément de butée (10a, 10b) est constitué en fer sur le côté tourné vers le piston (2), et est constitué en matériau élastomère sur le côté tourné vers le couvercle de cylindre (5a, 5b).
  6. Cylindre pneumatique à amortissement de fin de course selon l'une des revendications précédentes, caractérisé en ce que l'ouverture (12a, 12b) qui correspond à l'élément de butée (10a, 10b) de forme annulaire est formée par une fente annulaire ou par une série de trous agencés sous forme d'un cercle.
  7. Cylindre pneumatique à amortissement de fin de course selon la revendication 1, caractérisé en ce que l'élément magnétique (16a, 16b) déplaçable le long du boítier de cylindre (1) pour déterminer la longueur d'amortissement est un aimant permanent.
  8. Cylindre pneumatique à amortissement de fin de course selon la revendication 1, caractérisé en ce que l'élément magnétique (16a, 16b) déplaçable le long du boítier de cylindre (1) pour déterminer la longueur d'amortissement est une bobine magnétique électrique.
  9. Cylindre pneumatique à amortissement de fin de course selon l'une des revendications précédentes, caractérisé en ce qu'une tige de piston (6) dépasse depuis au moins un côté frontal du piston (2), ladite tige traversant de façon étanchée un couvercle de cylindre (5b) associé, ou en ce que le piston coopère avec des moyens pour former un cylindre dépourvu de tige de piston.
  10. Cylindre pneumatique à amortissement de fin de course selon l'une des revendications précédentes, caractérisé en ce que la chambre à pression (4a, 4b) destinée à produire la force peut être alimentée en air comprimé via un raccord extérieur (9a, 9b) pour la production d'une force, ou contient un élément à ressort pour la production d'une force.
EP20040100496 2003-02-12 2004-02-10 Cylindre à amortissement de fin de course réglable Expired - Lifetime EP1447571B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2003105954 DE10305954B3 (de) 2003-02-12 2003-02-12 Endlagengedämpfter Pneumatikzylinder mit verstellbarer Endlagendämpfung
DE10305954 2003-02-12

Publications (2)

Publication Number Publication Date
EP1447571A1 EP1447571A1 (fr) 2004-08-18
EP1447571B1 true EP1447571B1 (fr) 2005-09-07

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ID=32404441

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EP20040100496 Expired - Lifetime EP1447571B1 (fr) 2003-02-12 2004-02-10 Cylindre à amortissement de fin de course réglable

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EP (1) EP1447571B1 (fr)
DE (2) DE10305954B3 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1918592A1 (fr) * 2006-11-03 2008-05-07 Carl Freudenberg KG Joint d'étanchéité avec amortisseur de fin de course, fond avec joint d'étanchéité et vérin pneumatique avec fond et joint d'étanchéité
EP2107256A1 (fr) 2008-03-31 2009-10-07 Carl Freudenberg KG Vérin pneumatique à fin de course amortie
EP2107255A1 (fr) 2008-03-31 2009-10-07 Carl Freudenberg KG Vérin pneumatique à fin de course amortie
DE102017117000A1 (de) * 2017-07-27 2019-01-31 Schunk Gmbh & Co. Kg Spann- Und Greiftechnik Verfahren zum Steuern eines Aktuators sowie Aktuator

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1729015A1 (fr) 2005-06-03 2006-12-06 FESTO AG & Co Dispositif entraîné par un fluide
CN101504019B (zh) * 2008-12-17 2012-05-02 国营第三八八厂 一种永磁缓冲液压缸
DE102009034790B4 (de) * 2009-07-25 2024-02-01 Aventics Gmbh Zylinder mit Endlagendämpfung
DE102010015081A1 (de) 2010-04-15 2011-10-20 Robert Bosch Gmbh Endlagengedämpfter Druckmittelzylinder
CN105422542B (zh) * 2015-12-22 2017-07-28 扬州捷迈锻压机械有限公司 一种双层退料气缸
CN109530652A (zh) * 2018-11-08 2019-03-29 贵州华昌汽车电器有限公司 一种压铸模具用的接插式不锈钢感应油缸

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06100208B2 (ja) * 1987-05-29 1994-12-12 シ−ケ−デイ株式会社 流体圧シリンダ
DE4322255C2 (de) * 1993-07-05 1996-02-01 Festo Kg Dämpfungsvorrichtung
DE4410103C1 (de) * 1994-03-21 1995-08-31 Mannesmann Ag Antrieb der fluidischen oder elektrischen Bauart mit einer Steuerung
DE19645701A1 (de) * 1996-11-06 1998-05-07 Wabco Gmbh Ventileinrichtung für eine durch ein Druckmittel betätigbare Türanlage
DE29706364U1 (de) * 1997-04-10 1997-06-19 Bümach Engineering International B.V., Emmen Endlagengedämpfter Arbeitszylinder

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1918592A1 (fr) * 2006-11-03 2008-05-07 Carl Freudenberg KG Joint d'étanchéité avec amortisseur de fin de course, fond avec joint d'étanchéité et vérin pneumatique avec fond et joint d'étanchéité
EP2107256A1 (fr) 2008-03-31 2009-10-07 Carl Freudenberg KG Vérin pneumatique à fin de course amortie
EP2107255A1 (fr) 2008-03-31 2009-10-07 Carl Freudenberg KG Vérin pneumatique à fin de course amortie
DE102017117000A1 (de) * 2017-07-27 2019-01-31 Schunk Gmbh & Co. Kg Spann- Und Greiftechnik Verfahren zum Steuern eines Aktuators sowie Aktuator

Also Published As

Publication number Publication date
DE502004000056D1 (de) 2005-10-13
EP1447571A1 (fr) 2004-08-18
DE10305954B3 (de) 2004-07-01

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