EP1416166B1 - Vérin pneumatique avec dispositif amortisseur de fin de course - Google Patents

Vérin pneumatique avec dispositif amortisseur de fin de course Download PDF

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Publication number
EP1416166B1
EP1416166B1 EP20030103653 EP03103653A EP1416166B1 EP 1416166 B1 EP1416166 B1 EP 1416166B1 EP 20030103653 EP20030103653 EP 20030103653 EP 03103653 A EP03103653 A EP 03103653A EP 1416166 B1 EP1416166 B1 EP 1416166B1
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EP
European Patent Office
Prior art keywords
piston
cylinder
travel
pneumatic cylinder
damping
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
EP20030103653
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German (de)
English (en)
Other versions
EP1416166A1 (fr
Inventor
Philippe Ducrettet
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.)
Bosch Rexroth AG
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Bosch Rexroth AG
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Publication date
Application filed by Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1416166A1 publication Critical patent/EP1416166A1/fr
Application granted granted Critical
Publication of EP1416166B1 publication Critical patent/EP1416166B1/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
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F15B15/227—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having an auxiliary cushioning piston within the main piston or the cylinder end face

Definitions

  • the invention relates to a endlagengedämpften pneumatic cylinder with a through end cap cylinder closed cylinder housing in which a piston over a at least one-sided Druckschbeetzschung is arranged axially movable, on which a piston rod is attached, which seals at least one of the cylinder cover penetrates, further comprising means for cushioning the piston are provided.
  • Such pneumatic cylinders are used as a linear drive unit in many areas of the Mechanical and plant engineering, especially in handling technology used.
  • a End position damping is required for a pneumatic cylinder when the concrete Application case controlled lowering of the stroke speed shortly before reaching the end position requires.
  • the stress on the pneumatic cylinder is reduced and it will be Vibrations in the support structure in which the pneumatic cylinder is installed, reduced.
  • a reliably functioning cushioning is especially at Applications with high speeds and large masses necessary.
  • a first principle is used an elastomeric body to realize a simple stop cushioning.
  • shock absorbers are used.
  • the third principle uses a purely pneumatic damping.
  • the present invention is the latter Assign pneumatic damping principle.
  • the pneumatic cylinder corresponds to the Standard DIN ISO 6431 and consists essentially of a tubular Cylinder housing, which is closed on both sides with cylinder covers. The two Cylinder covers are detachably fastened to the cylinder housing via four external tie rods. Within the cylinder housing is a piston acted upon by pressure medium on both sides arranged. The pressure medium is applied here in the two cylinder covers each trained pressure medium connections. From the piston extends a piston rod, which the one cylinder cap sealed penetrates to the over the Pressure medium applied to direct the generated linear force to the outside. Further is the pneumatic cylinder is equipped with pneumatic cushioning on both sides.
  • EP 1 041 293 A2 is a generic endlagengedämpfter pneumatic cylinder out.
  • For double-end cushioning are two slidably mounted on the piston Sockets provided on the piston via a coil spring from the end face is attached protruding.
  • the bushing is overcoming the spiral spring generated reaction force in the piston retractable.
  • the so arranged on the piston socket accomplishes the cushioning by closing a corresponding annular exhaust port as the main flow cross section in the associated cylinder cover, so that in the Endlagendämpfungs Scheme only a parallel further exhaust port smaller diameter remains, which by a delay of the air outlet the End position damping causes.
  • the length of Endanschlagsweg Schemes is here by the Length of the spiral spring determined.
  • a disadvantage of this solution is the susceptibility to corrosion the spring made of a spring steel spiral spring.
  • Humidity of the compressed air can for Oxidation of the coil spring lead, which in extreme cases to the break of the coil spring after certain Operating time and thus can lead to failure of the end position damping.
  • This hollow cylinder section requires space in the form of a corresponding recess on the part of the associated cylinder cover, so that the width of the cylinder cover depends on the desired damping length.
  • this solution for a cushioning so also leads to a fairly large Length of the pneumatic cylinder.
  • US 2,642,845 discloses another solution for a Endlagegedämpften Pneumatic cylinder.
  • cushioning used here is a piston attached approximately hat-shaped rubber sleeve, which in the same manner as in the above-explained State of the art cooperates with the associated cylinder cover to the To realize cushioning.
  • a disadvantage of this solution is that the Rubber boot can lose elasticity after prolonged use, so that the Available damping length because of the occurring Material fatigue phenomena shortened after longer service life.
  • the object of the present invention to provide a pneumatic cylinder, the reliable acting pneumatic means for cushioning has the simple are constructed and do not increase the length of the pneumatic cylinder.
  • the invention includes the technical teaching that the means for cushioning a coaxially slidably mounted on the piston sleeve, which in the starting position protruding from an end face of the piston and overcoming a Reaction force in the piston is retractable, wherein the distal end of the bushing the End position damping by closing a corresponding annular Exhaust opening as the main flow cross section in the associated cylinder lid initiates, so that in Endanschlagsweg Switzerland only a parallel exhaust port as Remaining flow cross section remains.
  • the advantage of the solution according to the invention is in particular that on the part of the Cylinder on additional recesses for receiving components of the End position damping can be completely dispensed with.
  • the cylinder cover can be right be formed flat, so that the overall length of the endlagegedämpften Pneumatic cylinder is minimal.
  • the attenuation path determining Components of the end position damping integrated into the piston.
  • many individual components for the production of both Variants are used. This refers in particular to the production of the Cylinder housing and the piston rods, which are identical for both variants Application can come.
  • Another advantage of the invention is that the provided by the piston means for cushioning in a simple manner in Injection molding of plastic are manufacturable, which significantly reduces the manufacturing cost lowers.
  • the Endlagendämpfung proves to be extremely robust, since this completely according to Art realized a pneumatic principle.
  • the reaction force which brings and holds the bush in the extended starting position, is to be dimensioned so that a reliable extension of the socket from the retracted position is guaranteed out.
  • the reaction force is via one in the piston trained opposite the bush rear chamber applied, which has a Pressure medium applied to the piston driving cylinder chamber with acted upon becomes.
  • the admission of the rear pressure chamber by means of a for Cylinder chamber leading through simple through-hole can be realized in the piston.
  • reaction force via a piston used in and to apply the bushing acting on the rear compression spring.
  • the piston is for Housing the piston-side means for cushioning constructed in several parts.
  • the piston consists of a support member which connects to the piston rod manufactures. This can be done by screwing or pressing the piston rod into one Corresponding coaxial recess in the carrier part done.
  • the guide part forms a part of the inside radially rearward pressure chamber in which the sleeve is mounted axially displaceable.
  • the degree of damping of the end position damping can by means of a cylinder cover to be arranged manually adjustable damping screw can be realized adjustable by via a screwing in or out of the damping screw a corresponding change the residual flow cross-section of the parallel exhaust port.
  • the inventive means for cushioning can in a pneumatic cylinder either provided only by a cylinder cover or both sides of the cylinder cover become. It is so far a combination with differently constructed means for End position damping possible with one and the same pneumatic cylinder.
  • An alternative Means for cushioning represents, for example, the above-explained pneumatic Locking Radiator Lip Seal Concept.
  • the endlagengedämpfte pneumatic cylinder according to Figure 1 consists essentially of an extruded cylinder housing 1 made of light metal, the end face side with Cylinder covers 2 and 3 is closed. Both cylinder covers 2 and 3 are about diverse Screwed screws 4 to the cylinder housing 1.
  • Within the cylinder housing 1 is a Piston 5 mounted axially movable. From the piston 5 from a piston rod 6, which runs the a cylinder cover 2 penetrates sealed by a through hole 7. The Piston rod 6 performs a retraction movement in the pneumatic cylinder when the piston 5 via a formed in the cylinder cover 2 pressure medium connection 8 with compressed air is charged. Analogously, the piston rod 6 performs an extension movement when the piston 5 is acted upon via the pressure medium connection 3 with compressed air.
  • the present pneumatic cylinder double acting.
  • the pneumatic cylinder is equipped with a double-sided cushioning, wherein each cylinder cover 2 and 3 corresponding damping screws 10 and 11 for Setting the degree of damping are assigned.
  • the two damping screws 10 and 11 are in corresponding - not visible here - threaded sections Can be screwed in to narrow the channel.
  • the inventive means for cushioning are only here one-sided, namely provided on the sides of the cylinder cover 2. These have one on the piston 5 slidably mounted socket 12.
  • the socket 12 is here in its starting position shown and is from the cylinder cover 2 toward facing end face 13 of the Piston 5 forth.
  • the dimension X determines the Endanschlagsweg Scheme in which the Damping works.
  • the bushing 12 is retractable within a piston 5 formed in the rearward pressure chamber 14 stored.
  • the piston 5 consists in detail of a Support member 15 which is pressed or screwed tightly on the piston rod 6.
  • an annular guide member 16 is attached. External radial on the guide member 16 is a elastomeric piston seal 17 is held.
  • the piston seal 17 seals the piston 5 from the inner wall of the cylinder housing 1 from.
  • Inner Radial is through the Shaping the guide member 16 a majority of the rear pressure chamber 14 of the socket 12 formed. Between the support member 15 and the guide member 16 is still a circumferential outer radial groove formed, which for receiving an annular Magnet 19 is used.
  • the magnet 19 is part of a known electronic Device for detecting the piston position via a corresponding inductive induction sensor.
  • the annular magnet 19 is covered by a guide band 18 to the sliding friction between the piston 5 and the inner wall of the cylinder housing 1 to minimize.
  • the bush closes 12 via an end face side arranged annular seal 22 an annular Exhaust port 27, which the main flow cross-section for the out of the cylinder chamber 20th forms escaping exhaust air.
  • the Endlagendämpfung sets in that only the right lower residual flow cross-section of the remaining parallel exhaust port 24 to Available.
  • the pressure increases in the room 23, the speed of the piston rod 6 decreases. In the course of cushioning the bush 12 is in the pressure chamber 14 of the piston 15 is moved until finally the piston 5 with its end face 13 completely on the cylinder cover 2 comes to rest.

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

Claims (8)

  1. Vérin pneumatique amorti en fin de course, comportant un boítier de vérin (1) refermé par des couvercles de vérin (2, 3) côté extrémité, dans lequel un piston (5) est agencé avec faculté de déplacement axial par une alimentation au moins unilatérale en fluide sous pression, sur lequel est agencée une tige de piston (6) qui traverse avec étanchement l'un au moins des couvercles de vérin (2), des moyens étant prévus pour amortir le piston (5) en fin de course, qui comprennent une douille (12) fixée de façon déplaçable coaxialement sur le piston (5), laquelle fait saillie, en position de départ, d'une surface latérale frontale (13) du piston (5) et est susceptible d'être rétractée dans le piston (5) en surmontant une force de réaction, l'extrémité distale de la douille (12) provoquant l'amortissement en fin de course par fermeture d'une ouverture annulaire correspondante de sortie d'air (27) à titre de section d'écoulement principale dans le couvercle de vérin associé (2), de sorte que dans la zone d'approche de butée finale (X), il reste uniquement une ouverture parallèle de sortie d'air (24) en tant que section d'écoulement résiduelle,
    caractérisé en ce que la force de réaction peut être fournie par une chambre de pression (14) réalisée dans le piston (5) et située à l'arrière par rapport à la douille (12), chambre qui est susceptible d'être alimentée par une alimentation en fluide sous pression de la chambre de vérin (20) entraínant le piston (5).
  2. Vérin pneumatique amorti en fin de course selon la revendication 1, caractérisé en ce que l'alimentation de la chambre de pression arrière (14) est réalisée lors de l'alimentation de la chambre de vérin (20) au moyen d'un perçage traversant (21) ménagé dans le piston (5) et reliant la chambre de pression (14) à la chambre de vérin (20).
  3. Vérin pneumatique amorti en fin de course selon l'une des revendications précédentes, caractérisé en ce qu'il est prévu à l'extrémité distale de la douille (12) un joint élastomère (22) à la manière d'un joint torique.
  4. Vérin pneumatique amorti en fin de course selon l'une des revendications précédentes, caractérisé en ce que le piston (5) conçu de plusieurs pièces comprend un élément porteur (15) qui établit la liaison vers la tige de piston (6), et en ce qu'il est prévu un élément de guidage annulaire (16) fixé sur l'élément porteur (15) et destiné à la réception radialement extérieure d'un joint élastomère (17) du piston, élément de guidage qui forme radialement à l'intérieur au moins une partie de la chambre de pression arrière (14) dans laquelle est agencée la douille (12) avec faculté de translation axiale.
  5. Vérin pneumatique amorti en fin de course selon la revendication 4, caractérisé en ce que le piston (5) présente en outre une gorge radialement extérieure ménagée entre l'élément porteur (15) et l'élément de guidage (16) et destinée à recevoir un aimant annulaire (17) pour la détection inductive de la position du piston.
  6. Vérin pneumatique amorti en fin de course selon la revendication 5, caractérisé en ce que la gorge pourvue de l'aimant (19) est refermée par une bande de guidage (18) pour minimiser la friction par glissement entre le piston (5) et le boítier de vérin (1).
  7. Vérin pneumatique amorti en fin de course selon l'une des revendications précédentes, caractérisé en ce que pour régler le taux d'amortissement, il est prévu une vis d'amortissement (10, 11) qui est agencée dans le couvercle de vérin (2, 3) et dont le vissage ou dévissage modifie la section d'écoulement de l'ouverture de sortie d'air (24).
  8. Vérin pneumatique amorti en fin de course selon l'une des revendications précédentes, caractérisé en ce que les moyens destinés à l'amortissement en fin de course sont prévus du côté d'un couvercle de vérin (2) ou du côté des deux couvercles de vérin (2, 3).
EP20030103653 2002-10-07 2003-10-02 Vérin pneumatique avec dispositif amortisseur de fin de course Expired - Lifetime EP1416166B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10246766 2002-10-07
DE2002146766 DE10246766B3 (de) 2002-10-07 2002-10-07 Endlagengedämpfter Pneumatikzylinder

Publications (2)

Publication Number Publication Date
EP1416166A1 EP1416166A1 (fr) 2004-05-06
EP1416166B1 true EP1416166B1 (fr) 2005-12-28

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EP20030103653 Expired - Lifetime EP1416166B1 (fr) 2002-10-07 2003-10-02 Vérin pneumatique avec dispositif amortisseur de fin de course

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EP (1) EP1416166B1 (fr)
DE (2) DE10246766B3 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT504592B1 (de) * 2007-05-24 2008-06-15 Hoerbiger Origa Holding Ag Pneumatikzylinder mit einer und verfahren zur selbsteinstellenden endlagendämpfung
EP1998054B1 (fr) 2007-05-24 2014-08-13 Parker Origa Holding AG Cylindre pneumatique avec amortissement à réglage automatique en position finale et procédé
DE102010032359A1 (de) 2010-07-27 2012-02-02 Robert Bosch Gmbh Vorrichtung und Verfahren zur geschwindigkeitsabhängigen Endlagendämpfung eines Kolbens
CN111946587B (zh) * 2020-08-24 2022-04-22 中国石油化工集团有限公司 一种自卸压可调缓冲气体增压缸
DE102022134281A1 (de) 2022-12-21 2024-06-27 Amazonen-Werke H. Dreyer SE & Co. KG Fluidzylinder für eine landwirtschaftliche Maschine, sowie eine landwirtschaftliche Maschine

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2642845A (en) * 1950-12-20 1953-06-23 Westinghouse Air Brake Co Piston cushioning apparatus
FR1290632A (fr) * 1961-05-26 1962-04-13 Maxam Power Ltd Perfectionnements aux dispositifs à piston et cylindre pour moutons et appareils analogues actionnés par un fluide
DE7635587U1 (de) * 1976-11-11 1977-03-10 Festo-Maschinenfabrik Gottlieb Stoll, 7300 Esslingen Pneumatische oder hydraulische Kolbenzylinder-Einheit
DE3920293A1 (de) * 1989-06-21 1991-01-10 Festo Kg Kolben-zylinder-aggregat
DE9111000U1 (de) * 1991-09-05 1991-10-17 Hydraulik Techniek, Emmen Hydraulischer Hubzylinder
DE9111009U1 (de) * 1991-09-05 1993-01-14 Hydraulik Techniek, Emmen Hydraulikzylinder
US5309817A (en) * 1993-03-05 1994-05-10 Sims James O Linear brake for fluid actuator
DE29615799U1 (de) * 1996-09-11 1996-10-31 Festo Kg, 73734 Esslingen Vorrichtung zur Endlagendämpfung
DE29706364U1 (de) * 1997-04-10 1997-06-19 Bümach Engineering International B.V., Emmen Endlagengedämpfter Arbeitszylinder
IT1312235B1 (it) * 1999-03-29 2002-04-09 Luciano Migliori Dispositivo ammortizzatore per cilindri pneumatici.
JP2002048108A (ja) * 2000-08-04 2002-02-15 Smc Corp 位置検出センサの取付構造

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Publication number Publication date
DE10246766B3 (de) 2004-07-01
DE50302047D1 (de) 2006-02-02
EP1416166A1 (fr) 2004-05-06

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