EP0530541B1 - Cylindre hydraulique - Google Patents

Cylindre hydraulique Download PDF

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Publication number
EP0530541B1
EP0530541B1 EP92113537A EP92113537A EP0530541B1 EP 0530541 B1 EP0530541 B1 EP 0530541B1 EP 92113537 A EP92113537 A EP 92113537A EP 92113537 A EP92113537 A EP 92113537A EP 0530541 B1 EP0530541 B1 EP 0530541B1
Authority
EP
European Patent Office
Prior art keywords
damping
hydraulic cylinder
cylinder according
piston
groove
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
EP92113537A
Other languages
German (de)
English (en)
Other versions
EP0530541A1 (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.)
HYDRAULIK TECHNIEK
Original Assignee
HYDRAULIK TECHNIEK
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Filing date
Publication date
Application filed by HYDRAULIK TECHNIEK filed Critical HYDRAULIK TECHNIEK
Publication of EP0530541A1 publication Critical patent/EP0530541A1/fr
Application granted granted Critical
Publication of EP0530541B1 publication Critical patent/EP0530541B1/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 relates to a hydraulic cylinder with end position damping in a design according to the preamble of claim 1 as known from DE-A-3 415 829.
  • the stroke movement of the working piston is braked before reaching the respective stroke end position in that a damping attachment located in the direction of movement in front of the working piston with a reduced cross section compared to the piston diameter before reaching the stroke end prevents a direct outlet of the hydraulic medium from the respective pressure chamber in that the damping attachment in immerses a liquid-tight sliding engagement with a receiving bore located in the area of the respective cylinder end part, in the bottom area of which an outlet channel discharges the hydraulic medium via an adjustable throttle.
  • Such lifting cylinders are exposed to high wear in the area of the damping attachment and the receiving bore, and the arrangement of the throttle and a check valve in the respective cylinder end part is associated with a high level of construction expenditure, which adversely affects the production and operating costs
  • the invention provides a hydraulic cylinder with end position damping, which is achieved with simple means in that the hydraulic medium, as a damping means, can be discharged via the throttle groove from the area of the receiving bore in front of the respective cylinder end part and the spring chamber, the damping piston brought into support engagement on the cylinder end part for this purpose the safety of displacement of the working piston is increased in that the damping attachment can be introduced into the respective receiving bore independently of the guide.
  • the friction intensity is reduced by the working piston having an improved parallel guidance in the damping stroke range, so that with reduced wear a long-term stable function of the end position damping which increases the service life and reliability of such a hydraulic cylinder can be achieved.
  • FIG. 1 is a first embodiment of a hydraulic cylinder 1 in the end area of a working cylinder 2 with a cylinder bottom 3 forming a cylinder end part is illustrated in a partially sectioned illustration such that an inner working piston 4 is in a stroke position in front of a system in the area of the cylinder bottom 3 is made clear.
  • the cylinder base 3 is connected at the end to the working cylinder via a weld seam 5 in such a way that the cylinder base 3 partially, a pressure chamber 6 limiting, protrudes into the working cylinder 2.
  • a receiving bore 8 forming a blind hole is made in the cylinder base 3 in the center and symmetrically to a central plane 7 of the hydraulic cylinder 1.
  • this receiving bore 8 is assigned an axially offset damping projection 9 of the working piston 4, an outer diameter 10 of the damping projection 9 being dimensioned to a diameter 11 of the receiving bore 8 such that when they are paired, a sufficiently large outlet gap 12 (FIG. 3) is formed.
  • the bore 15 opens directly in front of a contact surface 16 of the cylinder base 3 in the pressure chamber 6.
  • the working piston 4 is arranged on a piston rod 17 which has a central head part 18, on which a piston bushing 21 having sealing sleeves 20 on the outer jacket is radially fixed by means of an axial holding member 19.
  • a damping piston 23, 23 ' which has a bore 22, 22' as a shaped recess, is arranged on each of the damping lugs 9, 9 'arranged symmetrically to the head part 18.
  • These damping pistons 23, 23 ' have a radial extension 24, 24' in the area of the bores 22, 22 'into which a compression spring 25, 25', which is supported in the area of the head part 18, engages in such a way that the damping pistons 23, 23 'counteract respective snap rings 26, 26 'are clamped.
  • the damping pistons 23, 23 ' are dimensioned in their axial length such that, under the action of the compression springs 25, 25', rear contact surfaces 27, 27 'of the damping pistons 23, 23' are spaced apart from floor surfaces 28, 28 'on the head part 18 that between a spring chamber 29, 29 'which can be filled with hydraulic medium is formed in each of these two surfaces. It is in the area of sliding surfaces 30, 30 'between the damping pistons 23, 23' and the piston bushing 21 of the working piston 4, an annular seal 31, 31 'sealing the spring chambers 29, 29' from the pressure chambers 6, 6 'is provided.
  • the damping pistons 23, 23 ' are each provided with a throttle groove 33, 33' on a face 32, 32 'facing the respective pressure chamber 6, 6', which is illustrated in more detail in FIGS. 4 and 5.
  • the respective throttle groove 33, 33 ' is advantageously designed in the form of a spiral, preferably as an Archimedean spiral, which has at least one winding section 35 which, starting from an annular groove 34, 34' at the front end of the bore 22, 22 ', leads into an edge region 36 of the respective end face 32, 32 '(FIG. 4).
  • a plurality of winding sections 35 starting from the annular groove 34, 34 ' can also be provided in the end face 32, 32'.
  • the spiral groove 33, 33 'expediently has a triangular cross-sectional shape 37, which is illustrated in the illustration according to FIG. 5 and is formed with a predetermined groove depth 38.
  • This cross-sectional shape 37 can optionally also be made variable in a round or polygonal embodiment, just as the groove depth 38 can be adapted to different operating conditions.
  • the working piston 4 is shown in two further stroke positions, each of which is achieved by a movement in an arrow direction 39.
  • the movement leads to the end face 32 of the damping piston 23 being fixed on the cylinder base 3 in the region of the contact surface 16 in an axial support engagement.
  • hydraulic medium e.g. after switching a hydraulic control (not shown), are introduced via the connection 14 into the pressure chamber 6, so that the piston 4 undergoes a reversal of the movement in the direction of arrow 39 and the damping piston 23 'in the region of an opposite cylinder head (not shown) with an analog End position damping can be brought to the system.
  • This damped lifting movement which is illustrated in principle in FIGS. 2 and 3, is associated with advantageously low frictional loads for the hydraulic cylinder 1, since only liquid friction occurs in the area of the outlet gap 12 and the frictional load in the area of the sliding surfaces 30, 30 'is reduced by the fact that this friction pairing of the damping piston 23 on the working piston 4 is in each damping stroke at a small radial distance from the outer sliding pair of the working piston 4 in the region of an inner wall 41 of the working cylinder 2 and the parallel guidance of the sliding parts thus achieved reduces the friction intensity to such an extent that the service life and the fluid tightness influence Intensities of wear are definitely excluded.
  • the hydraulic cylinder 1 is designed with two damping pistons 23, 23 ', each of which has a throttle groove 42, 42' in the area of the sliding surfaces 30, 30 '.
  • This support engagement which can possibly be improved by a sealing element (not shown), forms a sufficient sealing surface when the contact surface 16 of the cylinder base 3 touches the end surface 32 of the damping piston 23, so that the part remaining in the receiving bore 8 and in the spring chamber 29 remains separated, hydraulic medium connected in the area of the liquid-permeable bore 22 is only in flow connection with the (reduced) pressure chamber 6 via the throttle groove 42.
  • FIG. 8 illustrates an embodiment of the throttle groove 42 which, starting from a groove depth 44 'in the region of the end face 32 of the damping piston 23, merges into a groove depth 44' 'which is continuously increased towards the region of the bottom surface 28.
  • a constant reduction in the flow volume and thus an increased throttling of the speed of the hydraulic piston 4 can thus be achieved during the stroke movement of the damping piston 23 in the region of the end position damping.
  • a further variation of these damping properties is possible via the cross-sectional shape 45 of the respective throttle groove 42, 42 'as well as via the slope 43 (FIG. 9), which determines the distance between the throttle grooves 42, 42' in the lateral surface 46, 46 '.
  • the hydraulic cylinder 1 can be manufactured with the advantageously simple cylinder bottom 3 or cylinder head (not shown) overall with a reduced installation length, the simplified throttling of the pressure flow of the hydraulic medium in the stroke phase with end position damping substantially reducing the number of components, since both the installation of a adjustable throttle and a check valve can be omitted.

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)

Claims (17)

  1. Vérin hydraulique comportant un dispositif d'amortissement de fin de course pour un piston de travail (4) qui se déplace entre deux chambres de pression (6, 6') dans un cylindre de travail (2), et sur les deux côtés duquel est prévue à chaque fois une saillie d'amortissement (9, 9') s'avançant en position centrale, qui, avant que la fin de course correspondante soit atteinte, tout en étranglant une sortie directe du fluide hydraulique, peut être introduite par coulissement dans un alésage de réception (8) dans la zone d'une pièce de fermeture de cylindre (3) respective, caractérisé en ce que, dans une chambre à ressort (29, 29'), pouvant être remplie par le fluide hydraulique du piston de travail (4), dans la zone de la saillie d'amortissement (9, 9'), est installé un piston d'amortissement (23, 23') s'appuyant à coulissement contre un élément à ressort (25, 25') et dont la zone antérieure comporte une gorge d'étranglement (33, 33'; 42, 42') dont la face d'about (32, 32') peut être amenée, au moins dans la zone de la pièce de fermeture de cylindre (3), en contact d'appui séparant le fluide hydraulique présent dans l'alésage de réception (8) de la pièce de fermeture de cylindre (3) et dans la chambre à ressort (29, 29') de celui qui se trouve dans la chambre de pression correspondante (6, 6'), de sorte que la gorge d'étranglement (33, 33'; 42, 42') forme la seule liaison d'écoulement pour le fluide hydraulique séparé.
  2. Vérin hydraulique suivant la revendication 1, caractérisé en ce que la saillie d'amortissement (9, 9') présente un diamètre extérieur (10) ménageant un interstice de sortie (12) avec le diamètre (11) de l'alésage de réception (8) de la pièce de fermeture de vérin (3).
  3. Vérin hydraulique suivant la revendication 1 ou 2, caractérisé en ce que le piston d'amortissement (23, 23') présente un évidement façonné entourant la saillie d'amortissement (9, 9') et est mobile à coulissement entre une surface inférieure (28, 28') de la chambre à ressort (29, 29') et un jonc d'arrêt (26, 26') se trouvant dans la zone antérieure de la saillie d'amortissement (9, 9').
  4. Vérin hydraulique suivant la revendication 3, caractérisé en ce que l'évidement façonné a la forme d'un alésage (22, 22') permettant localement le passage du fluide et adapté au diamètre extérieur (10) de la saillie d'amortissement (9).
  5. Vérin hydraulique suivant la revendication 3 ou 4, caractérisé en ce que l'évidement façonné présente un élargissement radial (24, 24') logeant l'élément à ressort (25, 25').
  6. Vérin hydraulique suivant l'une quelconque des revendications 1 à 5, caractérisé en ce que la gorge d'étranglement (33, 33') est formée dans la face d'about (32, 32') du piston d'amortissement (23, 23').
  7. Vérin hydraulique suivant la revendication 6, caractérisé en ce que la gorge d'étranglement (33, 33') est en forme de spirale.
  8. Vérin hydraulique suivant la revendication 6 ou 7, caractérisé en ce que la gorge d'étranglement (33, 33'), partant d'une gorge circulaire (34, 34') à l'extrémité sur la face d'about de l'alésage (22, 22') du piston d'amortissement, est formée comme une section de spire (35) d'une spirale d'Archimède.
  9. Vérin hydraulique suivant l'une quelconque des revendications 6 à 8, caractérisé en ce qu'une gorge en spirale comportant plusieurs spires est formée dans la face d'about (32, 32').
  10. Vérin hydraulique suivant l'une quelconque des revendications 6 à 9, caractérisé en ce que la face d'about (32, 32') présente plusieurs sections de spires (35) partant de la gorge circulaire (34, 34').
  11. Vérin hydraulique suivant l'une quelconque des revendications 6 à 10, caractérisé en ce que la gorge d'étranglement (33, 33') présente une forme en coupe transversale (37) pointue, ronde ou polygonale avec une profondeur de gorge (38) prédéterminée.
  12. Vérin hydraulique suivant l'une quelconque des revendications 6 à 10, caractérisé en ce qu'un joint d'étanchéité annulaire (31, 31'), séparant de façon étanche la chambre à ressort (29, 29') de la chambre de pression (6, 6'), est prévu dans la zone d'une surface de glissement (30, 30') entre le piston d'amortissement (23, 23') et une virole de piston (21) du piston de travail (4).
  13. Vérin hydraulique suivant l'une quelconque des revendications 1 à 5, caractérisé en ce que la gorge d'étranglement (42, 42') est formée dans la zone de la surface de glissement (30, 30') du piston d'amortissement (23, 23').
  14. Vérin hydraulique suivant la revendication 13, caractérisé en ce que la gorge d'étranglement (42, 42') est en forme de filet hélicoïdal.
  15. Vérin hydraulique suivant la revendication 13 ou 14, caractérisé en ce que la gorge d'étranglement (42, 42') est prévue dans la surface cylindrique (46, 46') du piston d'amortissement (23, 23').
  16. Vérin hydraulique suivant l'une quelconque des revendications 13 à 15, caractérisé en ce que la gorge d'étranglement (42, 42') présente une pente (43) qui détermine le volume du fluide hydraulique en écoulement, de même qu'une forme en coupe transversale (45) pointue, polygonale ou ronde avec une profondeur de gorge (44) constante prédéterminée.
  17. Vérin hydraulique suivant les revendications 13 à 16, caractérisé en ce que la profondeur de gorge évolue depuis une faible profondeur de gorge (44') dans la zone de la face d'about (32, 32') vers une profondeur de gorge (44'') augmentant de façon continue dans la zone de la surface inférieure (28, 28').
EP92113537A 1991-09-05 1992-08-08 Cylindre hydraulique Expired - Lifetime EP0530541B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE9111009U DE9111009U1 (de) 1991-09-05 1991-09-05 Hydraulikzylinder
DE9111009U 1991-09-05

Publications (2)

Publication Number Publication Date
EP0530541A1 EP0530541A1 (fr) 1993-03-10
EP0530541B1 true EP0530541B1 (fr) 1995-07-19

Family

ID=6870949

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92113537A Expired - Lifetime EP0530541B1 (fr) 1991-09-05 1992-08-08 Cylindre hydraulique

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EP (1) EP0530541B1 (fr)
AT (1) ATE125336T1 (fr)
DE (2) DE9111009U1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19647472A1 (de) * 1996-11-16 1998-05-20 Zahnradfabrik Friedrichshafen Pneumatischer oder hydraulischer Stellmotor mit einer Abschalteinrichtung
NL1019112C2 (nl) * 2001-10-04 2003-04-07 Actuant Corp Hydraulische cilinder met eindstanddemping.
DE10246766B3 (de) * 2002-10-07 2004-07-01 Bosch Rexroth Ag Endlagengedämpfter Pneumatikzylinder
CN102108990B (zh) * 2010-07-23 2011-12-28 三一重工股份有限公司 一种液压油缸及液压缓冲系统、挖掘机和混凝土泵车
US11067104B1 (en) * 2020-11-16 2021-07-20 Caterpillar Inc. Integrated cylinder piston and bearing as a hydraulic cushion
CN114054705B (zh) * 2021-11-15 2023-06-13 马鞍山钢铁股份有限公司 结晶器液面稳定性控制方法

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3668975A (en) * 1970-10-13 1972-06-13 Int Harvester Co Decelerator means for expansible chamber device
DE2336066A1 (de) * 1973-07-16 1975-02-06 Wabco Westinghouse Gmbh Pneumatischer stellantrieb
US4250793A (en) * 1978-11-20 1981-02-17 Caterpillar Tractor Co. Cushioning device for fluid jacks
US4425836A (en) * 1981-02-20 1984-01-17 Government Innovators, Inc. Fluid pressure motor
DE3415829C2 (de) * 1984-04-27 1986-07-17 Emil Weber Fabrik für Ölhydraulik GmbH & Co, 7129 Güglingen Endlagendämpfung für einen hydraulischen Zylinder
DE3517564A1 (de) * 1985-05-15 1986-11-20 Friedrich 4970 Bad Oeynhausen Freimuth Vorrichtung zum bewegen von lasten
GB2186949A (en) * 1986-01-23 1987-08-26 Bespak P L C A flow control device

Also Published As

Publication number Publication date
ATE125336T1 (de) 1995-08-15
DE59202934D1 (de) 1995-08-24
EP0530541A1 (fr) 1993-03-10
DE9111009U1 (de) 1993-01-14

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