EP0684391B1 - Vérin à fluide sous pression - Google Patents

Vérin à fluide sous pression Download PDF

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Publication number
EP0684391B1
EP0684391B1 EP95105000A EP95105000A EP0684391B1 EP 0684391 B1 EP0684391 B1 EP 0684391B1 EP 95105000 A EP95105000 A EP 95105000A EP 95105000 A EP95105000 A EP 95105000A EP 0684391 B1 EP0684391 B1 EP 0684391B1
Authority
EP
European Patent Office
Prior art keywords
piston
cushioning
bushing
cylinder
piston rod
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
EP95105000A
Other languages
German (de)
English (en)
Other versions
EP0684391A1 (fr
Inventor
Alain Holovet
Frederic Pegaz
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0684391A1 publication Critical patent/EP0684391A1/fr
Application granted granted Critical
Publication of EP0684391B1 publication Critical patent/EP0684391B1/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
    • F15B15/222—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

  • the invention is based on a pressure medium actuable Working cylinder according to the preamble of claim 1 specified genus.
  • FR 24 79 389 A also includes a working cylinder Throttle device known in which a throttle bushing is fixed on the piston rod between a piston and a Piston rod section is clamped. On their outer The throttle bushing carries the entire surface area throttle grooves extending axially through their variable cross-section a progressive damping allow.
  • the damping bushing cannot be used here Check valve work so that as a result of Damping device no quick return stroke is possible.
  • the one fixed on the piston rod must Damping bush exactly on the housing side Passage opening in the cylinder head can be matched what construction costs increased.
  • DE 34 45 481 A1 also includes a working cylinder a damping device for a longitudinally movable guided and attached to a piston rod known to brake the piston when reaching an end position a damping bush between one Piston rod section and the piston is fixedly mounted into a suitable opening in the cylinder head can immerse to the unimpeded outflow of pressure medium from a cylinder chamber adjacent to the piston throttle or interrupt. Pressure medium can then only via a parallel connection with throttle screw flow to the cylinder connection. To the next Return stroke of the piston from its end position is sufficient large pressure medium flow the flow into the cylinder chamber To enable is in the damping bush plate-like check valve installed, which in one line connecting both sides of the damping bush axially and radially extending channels.
  • the working cylinder according to the invention with the characteristic Features of claim 1 has the advantage that he high damping effect with simpler and cheaper Construction achieved.
  • the working cylinder with Damping device comes with only a few parts and is also easy to manufacture. Furthermore, the Damping device from a rapid leakage of the piston its end position, so that relatively high Working speeds can be achieved with the working cylinder are. Furthermore, the damping device works relatively soft and avoids pressure surges, which too an unfavorable material load and thus one can lead to low lifespan.
  • FIG. 1 shows a longitudinal section through a Part of a pressure-operated cylinder
  • Figure 2 shows a partial section through the working cylinder Figure 1 in another working position, in which the Damping bush works as a check valve.
  • FIG. 1 shows a part of a pressure-medium-actuatable Working cylinder 10 in a half section, in which a Cylinder tube 11 with a cylinder cover 12 and one not a cylinder space 13 include in which a piston 14 is slidably guided.
  • the piston 14 is placed on a multiple Piston rod 15 attached via a in the cylinder cover arranged sealing sleeve 16 leads to the outside.
  • An annular space 17 is formed in the cylinder cover 12, the one in the radial direction with a cylinder connection 18th Has connection and in the axial direction via a annular passage opening 19 with a cylinder chamber 21, which is connected by the piston 14 in the cylinder space 13 is separated and from the piston 14 and the Cylinder cover 12 is limited.
  • the damping bushing 22 is essentially sleeve-shaped trained, their axial length about their Outer diameter corresponds and in particular a multiple their wall thickness is.
  • the damping bushing 22 has one first end face 29, which corresponds to the first stop 23 is facing and together with that as a valve seat working first annular shoulder 25 forms a seat valve 31, so that the damping bush 22 work as a check valve can.
  • the damping bushing 22 is on the first end face 29 chamfered on the outside to prevent the damping bushing 22 from breaking in to facilitate the passage opening 19. From the first End face 29 proceeding in the outer Shell surface 32 several throttle grooves 30, which are even are distributed along the circumference, in the axial direction run and near the other, second end face 33 of the Damping bushing 22 ends.
  • the damping bushing 22 is therefore part of a Damping device 38 in the cylinder 10, the Piston 10 a damped entry into its end position enables and on the other hand as fast as possible Permitted to run out of its end position.
  • One from Piston 14 and the cylinder bottom, not shown limited, second cylinder chamber is designated 39.
  • the operation of the working cylinder 10 is as follows explained, mainly on the function of Damping device 38 is received.
  • Pressure medium from the first cylinder chamber 21 can only throttled via the throttle grooves 30 to the cylinder connection 18th flow out.
  • throttle grooves 30 progressive damping can be achieved.
  • the relatively large radial play between the damping bushing 22 and Piston rod 15 allows a tight fit in the Passage opening 19 so that good damping values can be achieved are without the damping bush 22 tends to block.
  • FIG. 2 now shows in the partial longitudinal section of the Working cylinder 10 the facts when the piston 14 out an end position and thereby the function of Damping device 38 through the now as a check valve working damping bushing 22 is largely canceled to to achieve a quick extension.
  • the Cylinder port 18 pressurized in the Annulus 17 on the first end face 29 of the damping bush 22 acts. Due to the somewhat lower pressure level in the The first cylinder chamber 21, the damping bush 22 with its second end face 33 against the second stop 24 on Piston 14 pushed, whereby the seat valve 31 opens.
  • the damping device 38 By designing the damping device 38 with a only moving part, namely the damping bushing 22, can be a particularly effective and shock-free damping simple means.
  • the Damping bushing 22 By training the Damping bushing 22 as a movable seat valve member on which additionally the throttle grooves 30 and the pressure medium connection 35 are arranged, one can be particularly simple and inexpensive damping device to reach.

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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)

Claims (7)

  1. Vérin de travail (10) qui peut être actionné par un fluide sous pression, comprenant un piston (14)que l'on fait passer dans un espace cylindrique (13), piston qui est fixé sur une tige de piston (15) et qui peut coulisser dans l'espace cylindrique (13) entre deux positions terminales, et un dispositif d'amortissement qui sert à freiner le piston (14), lors de son mouvement dans une position terminale, un manchon d'amortissement (22) qui est disposé sur la tige (15) du piston, plongeant dans une ouverture de passage (19) et provoquant un écoulement étranglé du fluide sous pression à partir d'une chambre (21) du vérin, limitée par le piston (14)vers un raccord (18) du vérin pour obtenir une entrée lente du piston (14) dans sa position terminale, et un clapet anti-retour (31) associé au dispositif d'amortissement, clapet anti-retour (31) qui permet une mise en pression sans entrave de cette chambre (21) du vérin à partir du raccord (18) du vérin pour avoir une sortie rapide du piston (14) de sa position terminale, le manchon d'amortissement (22) étant guidé axialement et librement de façon mobile sur la tige (15) du piston entre deux butées (23, 24) situées du côté de la tige du piston, et une extrémité (29) du manchon d'amortissement (22) formant sur la butée (23)associée à l'ouverture de passage (19) la soupape (31) qui assume la fonction d'une soupape anti-retour, le manchon d'amortissement (22) étant constitué en forme de douille et l'une de ses faces frontales, la face (29) formant avec la butée (23), située du côté de la tige du piston, une soupape à siège (31), dans laquelle la liaison (35) pour le fluide sous pression qui est commandée par la soupape anti-retour (31), et qui s'étend entre les deux faces frontales (29, 33) du manchon d'amortissement (22), est disposée dans le manchon d'amortissement (22),
    caractérisé en ce que
    le manchon d'amortissement (22) présente sur sa surface enveloppe extérieure (32) des rainures d'étranglement (30) qui s'étendent sur toute sa longueur, et sont constituées pour obtenir un amortissement progressif, et
    la liaison pour le fluide sous pression est disposée entre deux faces frontales (29, 33)du manchon d'amortissement (22)dans sa paroi intérieure (37), manchon d'amortissement (22) que l'on fait passer directement sur la tige du piston (15).
  2. Vérin de travail selon la revendication 1,
    caractérisé en ce que
    la liaison (35) pour le fluide sous pression est formée par des rainures (36) qui s'étendent en forme d'hélice, dans la paroi intérieure (37) du manchon d'amortissement (22).
  3. Vérin de travail selon la revendication 1 ou 2,
    caractérisé en ce qu'
    on fait passer le manchon d'amortissement (22) avec un jeu radial relativement grand sur la tige (15) du piston.
  4. Vérin de travail selon l'une des revendications 1 à 3,
    caractérisé en ce que
    la tige (15) du piston se transforme au moyen d'un épaulement annulaire (25) en une section de guidage (26) qui a un plus petit diamètre, sur laquelle on fait passer le manchon d'amortissement (22) et
    cet épaulement annulaire (25) sert de siège de soupape et de butée (23).
  5. Vérin de travail selon la revendication 4,
    caractérisé en ce que
    la section de guidage (26) se transforme au moyen d'un deuxième épaulement annulaire (27) en une section de tige (28)sur laquelle est disposé le piston (14) qui de son côté forme la deuxième butée (24) du manchon d'amortissement (22).
  6. Vérin de travail selon l'une des revendications 1 à 5,
    caractérisé en ce que
    l'orifice de passage (19) est disposé dans une culasse (12) et son diamètre est adapté au diamètre extérieur du manchon d'amortissement (22) et présente en particulier un jeu étroit.
  7. Vérin de travail selon l'une des revendications 1 à 6,
    caractérisé en ce que
    le manchon d'amortissement (22) en forme de douille présente des faces frontales (29, 33) de même grandeur, et sa longueur axiale correspond à peu près à son diamètre extérieur, en particulier atteint un multiple de l'épaisseur de paroi du manchon d'amortissement (22).
EP95105000A 1994-04-26 1995-04-04 Vérin à fluide sous pression Expired - Lifetime EP0684391B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4414485 1994-04-26
DE4414485A DE4414485A1 (de) 1994-04-26 1994-04-26 Druckmittelbetätigbarer Arbeitszylinder

Publications (2)

Publication Number Publication Date
EP0684391A1 EP0684391A1 (fr) 1995-11-29
EP0684391B1 true EP0684391B1 (fr) 1999-12-08

Family

ID=6516445

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95105000A Expired - Lifetime EP0684391B1 (fr) 1994-04-26 1995-04-04 Vérin à fluide sous pression

Country Status (2)

Country Link
EP (1) EP0684391B1 (fr)
DE (2) DE4414485A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19635876C2 (de) * 1996-09-04 2001-04-05 Orenstein & Koppel Ag Ringseitige Dämpfung an druckmittelbetätigten Arbeitszylindern
DE29618186U1 (de) * 1996-10-21 1998-02-19 Bosch Gmbh Robert Druckmittelbetätigbarer Arbeitszylinder
AT406292B (de) * 1998-07-22 2000-03-27 Hainzl Industriesysteme Ges M Vorrichtung zum abbremsen eines kolbens eines hydraulikzylinders
KR100652872B1 (ko) * 2005-01-03 2006-12-01 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 실린더 쿠션장치
DE102010024505A1 (de) * 2010-06-21 2011-12-22 Pacoma Gmbh Endlagengedämpfter Druckmittelzylinder

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2433662A1 (fr) * 1978-08-18 1980-03-14 Outillage Air Comprime Clapet a bille
US4424737A (en) * 1980-03-26 1984-01-10 Kabushiki Kaisha Komatsu Seisakusho Stroke cushioning apparatus for hydraulic cylinders
DE3445481A1 (de) * 1983-12-16 1985-06-27 E.A. Storz Gmbh & Co Kg, 7200 Tuttlingen Hydraulikzylinderaggregat
GB9225925D0 (en) * 1992-12-11 1993-02-03 Parker Hannifin Plc Improvements relating to cylinders

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
Firmenschrift 'Marrel Hydro Catalogue 11085F - 11/79', Seiten 1-7 *

Also Published As

Publication number Publication date
DE4414485A1 (de) 1995-11-02
DE59507364D1 (de) 2000-01-13
EP0684391A1 (fr) 1995-11-29

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