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EP1744062B1 - Vérin avec amortissement de fin de course - Google Patents

Vérin avec amortissement de fin de course Download PDF

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Publication number
EP1744062B1
EP1744062B1 EP06012469A EP06012469A EP1744062B1 EP 1744062 B1 EP1744062 B1 EP 1744062B1 EP 06012469 A EP06012469 A EP 06012469A EP 06012469 A EP06012469 A EP 06012469A EP 1744062 B1 EP1744062 B1 EP 1744062B1
Authority
EP
European Patent Office
Prior art keywords
piston
damping
cylinder according
actuator cylinder
end part
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.)
Not-in-force
Application number
EP06012469A
Other languages
German (de)
English (en)
Other versions
EP1744062A2 (fr
EP1744062A3 (fr
Inventor
Ralph Riedel
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.)
Norgren GmbH
Original Assignee
Norgren GmbH
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 Norgren GmbH filed Critical Norgren GmbH
Publication of EP1744062A2 publication Critical patent/EP1744062A2/fr
Publication of EP1744062A3 publication Critical patent/EP1744062A3/fr
Application granted granted Critical
Publication of EP1744062B1 publication Critical patent/EP1744062B1/fr
Not-in-force 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
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/082—Characterised by the construction of the motor unit the motor being of the slotted cylinder type
    • 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
    • F15B15/222—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 throttles the main fluid outlet as the piston approaches its end position

Definitions

  • pressure-actuated working cylinders are often designed with a Endlagendämfpung to ensure a bumpless working of the cylinder.
  • An example of such a fluid-actuated cylinder with cushioning is in the U.S. Patent 6,758,127 described.
  • an axially projecting tubular, cylindrical damping pin is provided on both sides of the piston, in the end piece facing it the cylinder body is associated with a receiving opening, in which the damping pin is immersed in the approach of the piston to its end position.
  • the receiving opening is connected to a device for throttled discharge of trapped in the damping chamber pressure medium. This device may for example have a throttle valve.
  • damping stroke The path length, the piston covers when approaching an end position from the position in which the damping pin begins to penetrate straight into the receiving opening and the damping chamber closes up to the position in which the piston has reached its actual end position and, for example, with its end face rests on the end face of the associated end part, is referred to as damping stroke.
  • the length of this damping stroke is determined by the axial length of the damping pin and thus the depth of the receiving opening, which in turn is limited by the axial dimensions, ie the thickness of the end portion. Since the installation length of a working cylinder is often specified, for example by standards, for a given piston stroke and the damping stroke can not be made arbitrarily large.
  • the spool also serves as a shut-off valve and valve for outflow, wherein forms a damping reservoir in the system of the control piston at the respective end portion of the working cylinder, from the fluid via a throttled Abströmbohrung can flow out. While this cylinder has a longer damping travel or stroke compared to the prior art, the cone spring requires additional installation space, except that the use of spring elements is problematic in many applications because of their limited life.
  • the means for damping the movement of the piston when approaching at least one of its end positions comprises two cooperating damping elements, one of which is provided on one end portion of the working cylinder and the other on the piston on its end portion facing side.
  • the two damping elements close at the approach of the piston to its end position a damping chamber, which is connected to a device for throttled discharge of trapped in the damping chamber pressure medium.
  • the two damping elements in the direction of the piston movement are axially inserted into one another by one of the two damping elements has a receiving opening formed in the end portion and the other has a sealingly inserted into the receiving opening damping pin.
  • the damping pin has a sleeve which is mounted axially displaceably limited axially on a rod-shaped bearing part projecting axially from the piston and which is directly part of the piston rod.
  • the object of the invention is therefore a working cylinder to provide cushioning, the damping device is characterized by a simple, reliable construction and with limited installation length of the entire working cylinder has a large damping stroke.
  • the working cylinder according to the invention has the features of claim 1.
  • both damping elements are provided with cooperating inhibiting means under the action of the longitudinally displaceable damping element is adjustable in a movement of the piston from its end position to an end position which is further away from the piston or the end portion as a first end position, the Damping element normally occupies.
  • the displaceability of the one damping element with respect to the piston or the end part results in an additional damping stroke by a telescopic action of the telescoping action of the piston as it approaches its end position.
  • the inhibitor ensures that when the path Piston from its end position, the longitudinally displaceable damping element returns to its original position, without the need for additional actuators, such as spring elements or the like. This also no additional installation space is required.
  • the simple design also allows the use of near-serial parts for large damping strokes, ie long damping paths.
  • the working cylinder can be both a single-acting and double-acting working cylinder with a piston rod brought out through at least one of its end parts, but the idea according to the invention can equally be applied to rodless cylinders.
  • the working cylinders are usually pressure medium actuated, for example. Pneumatic cylinder, but a corresponding device for cushioning can also be provided in working cylinders or linear drives, which have a different form of operation, for example. Over cables and the like.
  • FIGS. 1 to 7 illustrate a working cylinder in the form of a pneumatic cylinder having a cylinder body in the form of a cylinder tube 1 and two sealed with the cylinder tube 1 end portions 2, 3.
  • the cylinder tube 1 encloses a cylinder space in which a piston 4 is guided longitudinally displaceable, which is sealed against the inner wall of the cylinder tube 1 via piston ring seals 5.
  • the piston 4 divides the cylinder space into two cylinder or pressure chambers 6, 7, which are separated by the piston 4.
  • a coaxial cylindrical piston rod 8 is fixedly connected, which is sealed by the end part 2 is guided by.
  • a piston rod seal is illustrated at 9.
  • the cylinder chamber 6 passing through the piston rod 8 is extended on the opposite side of the piston.
  • On its extension 10 a coaxial cylindrical sleeve 11 is placed, which projects into the cylinder chamber 7 and is fixed by a 12 indicated, bolted to the piston rod extension 10 screw on the piston 4.
  • each opening into a threaded bore 13 connecting channel 14 is formed, which via a corresponding screwed connection fitting with a compressed air source not shown or a vent, in each case via corresponding, also not shown valves, can be connected and opens on its other side in each case in a cylindrical, cup-shaped receiving opening 15, which opens on the piston 4 side facing the respective end portion 2 and 3 to the cylinder chamber 6 and 7 out.
  • the coaxial to the piston rod receiving opening 15 is closed in both end portions 2, 3 on the side facing away from the piston 4, which is achieved at the end part 2 by the piston rod seal 9, while the receiving opening 15 in the other end part 3 by a molded-bottom part 16th is completed.
  • Each of the two receiving openings 15 includes an inserted into an annular groove 18 in the vicinity of its mouth, around running elastic sealing element in the form of an O-ring 20th
  • the axial depth of the two receiving openings 15 is usually the same and dimensioned so that there is a maximum depth 21 without lengthening the installation length of the working cylinder.
  • the receiving opening 15 in each of the two end portions 2, 3 each forms a damping element of a device for cushioning the piston 4. It cooperates for this purpose with a second damping element, which is provided on the piston 4 and each having a telescopic damping pin which at the approach of the piston at its respective end position in the respective receiving opening 15 is sealingly inserted to limit a damping chamber, the pressure medium includes, which causes a throttling of the piston movement in the throttled outflow from the receiving opening a pneumatic damping.
  • the cooperating with the receiving opening 15 second damping element has a cylindrical sleeve 19 which is mounted on the end part 2 facing the side of the piston 4 on the piston rod 8 and on the other end part 3 facing the piston side on the cylindrical sleeve 11 each axially limited longitudinally displaceable.
  • the sleeve 19 is chamfered on its side facing the respective end part 2, 3 at 22 outside and at its opposite end with an annular flange 23 which carries a respective end portion 2, 3 facing stop surface 24.
  • the annular flange 23 of each of the two sleeves 19 is assigned in each case an annular groove 25 in the piston end face facing it, which can receive the annular flange 24 completely, as will be explained in detail yet.
  • each sleeve 19 is formed in the region of its inner wall with an annular shoulder 26 which cooperates with a corresponding annular shoulder 27 near the free end of the tube 11 on one side of the piston and an annular shoulder 28 on the piston rod 8 on the other side of the piston.
  • the annular shoulders 27, 28 are spaced so far from the respective adjacent piston face and tuned to the length of the sleeve 19, that in the in FIG.
  • the two sleeves 19 are releasably locked.
  • the associated latching device has an in an annular groove 29 and 30 of the piston rod 8 and the sleeve 11 inserted latching element in the form of an O-ring 31 which cooperates with a locking recess 32 on the inner wall of the sleeve 19 elastically yielding.
  • the end portion 3 adjacent sleeve 19 protrudes axially over a large part of its length over the sleeve 11, while the other sleeve 19 rests on a larger diameter portion of the piston rod 8 over most of its length.
  • locking can alternatively occur a frictional locking of the sleeves.
  • an all-round annular bead 32 is formed, which can cooperate with the respective O-ring 20 in the end part 2 and 3 and together with this inhibiting means for each of the respective End portion directed away axial movement of the sleeve 19 in the manner described below.
  • the two receiving openings 15 in the end parts 2, 3 are each provided with a device for throttled discharge of pressure medium enclosed in the damping space enclosed by the piston 4, the cylinder space or 7 and the end part 2 and 3, respectively.
  • this device includes a throttle valve 33, which in the detail "Y" of FIG. 2 is illustrated in its details.
  • the throttle valve 33 is inserted into a corresponding bore 34 of the respective end part 2 or 3, which via a coaxial channel 35 with the receiving opening 15 and a laterally outgoing channel 36th is in communication with the cylinder chamber 6 and 7, respectively.
  • the throttle valve 33 has a valve body 37 which is pressed by a valve spring 38 elastically against a valve seat 39, wherein the valve spring 39 is axially supported against a screwed into the bore 34 plug 40.
  • the valve body 37 is formed in the manner of a differential piston. If the same medium pressure prevails in the two channels 35, 36, then the valve spring 38 can keep the valve body 37 closed on the valve seat 39 and thus the throttle valve ( Fig. 2 ). If the pressure in the damping chamber, and thus in the channel 35, increases by a preset value, the valve body 37 is lifted off the seat 39 accordingly.
  • a throttle channel 40 of small cross-section is formed, through which air can flow out of the damping chamber into the adjacent pressureless cylinder chamber 6 or 7 when the valve is closed.
  • the throttle channel 40 acts as a bypass channel.
  • Rodless cylinders are known in various embodiments. Examples are in the EP 0 260 344 B1 and the US-A 4,373,427 described. In such working cylinders, the peg-shaped damping element is often firmly connected to the end parts of the cylinder, wherein the damping element during the movement of the piston against the end position enters into this. There are, as the US patent shows, reverse constructions have been proposed, but then leads to correspondingly thick end parts. If the damping element is arranged at the respective end part, the space already present in these working cylinders in the piston is advantageously utilized for the pneumatic damping and the end parts can be kept relatively short and independent of the damping length. The invention allows to achieve without extension of the installation length of the cylinder in these cases much longer damping paths as this FIG. 8 it can be seen conspicuously:
  • the tubular cylinder body 51 is closed at the ends by two end parts 52, 53 and encloses a cylinder space in which a piston 54 is guided longitudinally displaceable.
  • the cylinder body 51 is provided with a longitudinal slot through which a web connected to the piston 54 leads outwardly to a power transmission element 55.
  • the longitudinal slot is closed by an elastic sealing band 56 which is in two parts and which Cylinder or pressure chamber 57, 58 seals on both sides of the piston 54 to the outside.
  • Each of the two end portions 52 carries a projecting into the respective cylinder chamber 57 and 58, tubular bearing part 59, which is aligned coaxially with the piston 54.
  • On each bearing part 59 is a sleeve 19 corresponding to the FIGS. 1 to 7 mounted longitudinally displaceable, which is associated with a coaxial cylindrical receiving opening 15 in the opposite end face of the piston 54.
  • the sleeve 19 is as in particular in FIG. 3 represented, designed and stored. The same parts are provided with the same reference numerals and not explained again.
  • FIG. 8 shows the rodless cylinder in a stroke position in which the forming a damping element left sleeve 19 in the extended end position, that is shown away from the end portion 52. Again, holds a detent or possibly just a frictional engagement between the bearing part 59 and the sliding sleeve 19 formed by this, displaceable damping element in the extended position.
  • Upon movement of the piston in the direction of the left end position to the sleeve 19 is first inserted into the receiving opening 15, whereupon the sleeve itself on the bearing part 59 until it rests against the end part 52 is pushed telescopically.
  • a detent or a simple frictional engagement between the sleeve 19 and the inhibiting means forming O-ring 20 ensures that the sleeve 19 forming the displaceable damping element in a piston movement away from the end portion 52 in the in FIG. 8 shown extended end position is brought back.

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

Claims (22)

  1. Vérin avec amortissement de fin de course, comprenant un corps de vérin (1) contenant une chambre de vérin, deux pièces d'extrémité (2, 3 ; 52, 53) fermant la chambre de vérin à ses extrémités, un piston (4) monté coulissant longitudinalement entre deux fins de course dans la chambre de vérin, et un dispositif pour amortir le mouvement du piston à l'approche d'au moins une de ses fins de course, lequel dispositif comporte deux éléments d'amortissement (15, 19) qui coopèrent et dont l'un est prévu sur une pièce d'extrémité (2, 3 ; 52, 53) et l'autre sur le piston (4), du côté de celui-ci tourné vers la pièce d'extrémité, et au moyen desquels une chambre d'amortissement peut être fermée lorsque le piston s'approche de sa fin de course, laquelle chambre d'amortissement est reliée à un dispositif permettant l'évacuation contrôlée d'un fluide sous pression enfermé dans la chambre d'amortissement, les deux éléments d'amortissement étant conçus de manière insérable l'un dans l'autre axialement dans la direction de mouvement du piston, et au moins un (19) des éléments d'amortissement étant monté sur la pièce d'extrémité (52, 53) ou le piston (4) de manière à pouvoir coulisser longitudinalement de façon limitée par rapport au piston ou à la pièce d'extrémité entre deux positions extrêmes distantes l'une de l'autre axialement, caractérisé en ce que les deux éléments d'amortissement sont pourvus de moyens qui coopèrent sous la forme de moyens de blocage, sous l'effet desquels l'élément d'amortissement coulissant longitudinalement (19) peut être déplacé dans une première position extrême proche du piston (4) ou de la pièce d'extrémité (52, 53) lorsque le piston s'approche de sa fin de course et dans une deuxième position extrême, plus éloignée du piston (4) ou de la pièce d'extrémité (52, 53), lorsque le piston s'éloigne de sa fin de course.
  2. Vérin selon la revendication 1, caractérisé en ce que, sur les deux éléments d'amortissement, l'un présente une ouverture de réception (15) ménagée dans la pièce d'extrémité ou dans le piston et l'autre présente un tourillon amortisseur (11, 19 ; 59, 19) insérable télescopiquement de manière étanche dans l'ouverture de réception.
  3. Vérin selon la revendication 2, caractérisé en ce que le tourillon amortisseur comporte un manchon (19) qui est monté coulissant d'une façon limitée axialement sur une pièce de support (11, 59) en forme de tige qui dépasse axialement du piston ou de la pièce d'extrémité.
  4. Vérin selon la revendication 3, caractérisé en ce que la pièce de support fait partie d'une tige de piston (8) qui est reliée au piston (4) et qui sort axialement de la chambre de vérin à travers une pièce d'extrémité.
  5. Vérin selon la revendication 3, caractérisé en ce que la pièce de support comporte un tube (59) qui est relié à la pièce d'extrémité (52, 53) associée et dont l'intérieur est relié au dispositif d'évacuation contrôlée du fluide sous pression enfermé dans la chambre d'amortissement.
  6. Vérin selon une des revendications 3 à 5, caractérisé en ce que le manchon (19) est monté sur la pièce de support de manière à faire saillie axialement au-delà du côté frontal du piston (4) ou de la pièce d'extrémité (52, 53) tourné vers lui dans au moins une de ses positions extrêmes.
  7. Vérin selon la revendication 2, caractérisé en ce que des moyens de butée limitant la profondeur d'enfoncement du tourillon amortisseur (11, 19) dans l'ouverture de réception (15) sont associés à celui-ci.
  8. Vérin selon les revendications 3 et 7, caractérisé en ce que les moyens de butée comportent une surface de butée (24) qui est formée sur le manchon (19) et qui est disposée de manière à coopérer avec une surface de butée correspondante sur la pièce d'extrémité (2, 3) ou le piston (4).
  9. Vérin selon la revendication 8, caractérisé en ce que la surface de butée (24) est formée sur une bride annulaire (23) du manchon (19).
  10. Vérin selon la revendication 9, caractérisé en ce que la bride annulaire (23) est reçue dans un renfoncement (25) du côté frontal de la pièce d'extrémité (2,3) ou du piston (4) qui lui est associé lorsque le manchon (19) est entièrement enfoncé dans l'ouverture de réception (15).
  11. Vérin selon une des revendications précédentes, caractérisé en ce que, dans sa position de fin de course, le piston (4) s'applique essentiellement frontalement contre la pièce d'extrémité (52, 53) correspondante.
  12. Vérin selon la revendication 1, caractérisé en ce qu'il est prévu des moyens de blocage formés par un ajustement glissant par friction entre les deux éléments d'amortissement (15, 19) insérables l'un dans l'autre ou entre des pièces reliées à ceux-ci.
  13. Vérin selon la revendication 1, caractérisé en ce que les moyens de blocage comportent un encliquetage libérable entre les deux éléments d'amortissement (15, 19) insérables l'un dans l'autre ou entre des pièces reliées à ceux-ci.
  14. Vérin selon la revendication 12 ou 13, caractérisé en ce que les moyens de blocage comportent au moins un organe élastique (20) qui est formé sur un élément d'amortissement (15) et qui, lorsque le piston s'approche de sa fin de course, peut être amené en prise par friction avec une surface de l'autre élément d'amortissement (10).
  15. Vérin selon la revendication 14, caractérisé en ce que l'autre élément d'amortissement (19) comporte, sur sa surface, un dispositif d'encliquetage qui coopère avec l'organe élastique.
  16. Vérin selon la revendication 15, caractérisé en ce que le dispositif d'encliquetage comporte un bourrelet (32) ou un renfoncement disposé sur la surface.
  17. Vérin selon une des revendications précédentes, caractérisé en ce que l'élément d'amortissement coulissant longitudinalement (19) est maintenu par friction ou par force dans sa position extrême éloignée du piston ou de la pièce d'extrémité.
  18. Vérin selon une des revendications précédentes, caractérisé en ce que le dispositif d'évacuation contrôlée du fluide sous pression enfermé dans la chambre d'amortissement comprend une soupape de limitation de pression.
  19. Vérin selon la revendication 18, caractérisé en ce que la soupape de limitation de pression présente une valeur seuil réglable.
  20. Vérin selon la revendication 17 ou 18, caractérisé en ce qu'un canal d'évacuation de fluide sous pression (40) est disposé en parallèle avec la soupape de limitation de pression.
  21. Vérin selon une des revendications précédentes, caractérisé en ce qu'il s'agit d'un vérin à double effet avec un amortissement de fin de course dans chacune de ses deux positions de fin de course.
  22. Vérin selon une des revendications précédentes, caractérisé en ce qu'il est réalisé sans tige de piston.
EP06012469A 2005-07-14 2006-06-17 Vérin avec amortissement de fin de course Not-in-force EP1744062B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005032853A DE102005032853B3 (de) 2005-07-14 2005-07-14 Arbeitszylinder mit Endlagendämpfung

Publications (3)

Publication Number Publication Date
EP1744062A2 EP1744062A2 (fr) 2007-01-17
EP1744062A3 EP1744062A3 (fr) 2009-07-22
EP1744062B1 true EP1744062B1 (fr) 2011-11-23

Family

ID=37076268

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06012469A Not-in-force EP1744062B1 (fr) 2005-07-14 2006-06-17 Vérin avec amortissement de fin de course

Country Status (7)

Country Link
US (1) US7581485B2 (fr)
EP (1) EP1744062B1 (fr)
CN (1) CN1896552A (fr)
AT (1) ATE534825T1 (fr)
DE (1) DE102005032853B3 (fr)
DK (1) DK1744062T3 (fr)
ES (1) ES2378077T3 (fr)

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CN102705299A (zh) * 2012-05-17 2012-10-03 太仓奥科机械设备有限公司 气缸缓冲装置
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DE3818833A1 (de) * 1988-06-03 1989-02-02 Dimter Erwin Kolben fuer druckluftzylinder, insbesondere fuer kolbenstangenlose zylinder
SE467424B (sv) * 1990-11-09 1992-07-13 Mecman Ab Anordning foer aendlaegesdaempning och hastighetsreglering av roerelsen hos en kolv i en tryckmediecylinder
GB9421002D0 (en) * 1994-10-18 1994-12-07 Norgren Martonair Gmbh Fluid powered cylinder
DE29706364U1 (de) * 1997-04-10 1997-06-19 Bümach Engineering International B.V., Emmen Endlagengedämpfter Arbeitszylinder
JP3391241B2 (ja) * 1997-10-28 2003-03-31 日立建機株式会社 油圧シリンダのクッション装置
DE20021520U1 (de) * 2000-12-20 2001-03-01 IMI Norgren GmbH, 46519 Alpen Druckmediumsbetätigter Arbeitszylinder

Also Published As

Publication number Publication date
DE102005032853B3 (de) 2007-02-08
CN1896552A (zh) 2007-01-17
DK1744062T3 (da) 2011-12-19
ATE534825T1 (de) 2011-12-15
EP1744062A2 (fr) 2007-01-17
US7581485B2 (en) 2009-09-01
ES2378077T3 (es) 2012-04-04
EP1744062A3 (fr) 2009-07-22
US20070012532A1 (en) 2007-01-18

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