EP0427001B1 - Chariot élévateur avec un mât de levage disposé mobilement - Google Patents

Chariot élévateur avec un mât de levage disposé mobilement Download PDF

Info

Publication number
EP0427001B1
EP0427001B1 EP90119648A EP90119648A EP0427001B1 EP 0427001 B1 EP0427001 B1 EP 0427001B1 EP 90119648 A EP90119648 A EP 90119648A EP 90119648 A EP90119648 A EP 90119648A EP 0427001 B1 EP0427001 B1 EP 0427001B1
Authority
EP
European Patent Office
Prior art keywords
cylinder
piston
dampening
lift truck
lift
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
EP90119648A
Other languages
German (de)
English (en)
Other versions
EP0427001A1 (fr
Inventor
Rainer Dr.-Ing. Bruns
Friedrich Wilhelm Groll
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.)
Jungheinrich AG
Original Assignee
Jungheinrich AG
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
Priority claimed from DE19893937404 external-priority patent/DE3937404A1/de
Priority claimed from DE19904019075 external-priority patent/DE4019075C2/de
Priority claimed from DE9006695U external-priority patent/DE9006695U1/de
Application filed by Jungheinrich AG filed Critical Jungheinrich AG
Publication of EP0427001A1 publication Critical patent/EP0427001A1/fr
Application granted granted Critical
Publication of EP0427001B1 publication Critical patent/EP0427001B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
    • B66F9/075—Constructional features or details
    • B66F9/08—Masts; Guides; Chains
    • B66F9/082—Masts; Guides; Chains inclinable

Definitions

  • the invention relates to a stacking vehicle according to the preamble of patent claim 1.
  • the invention has for its object to provide an effective damping in a stacking vehicle with a movable mast, which ensures safe entry and exit in shelves even with the mast extended.
  • Stacking vehicles with horizontally movable mast are known per se. They are used, for example, in stacking vehicles, with which pallets and the like are removed from or stacked on shelves. With the invention it is prevented that more or less strong vibrations occur during the horizontal movement of the mast, which impair the stacking or removal of the loads. Such an oscillation not only acts in the horizontal direction, but also leads to pivoting of the mast, which changes the position of the load carrying device (fork).
  • a damping arrangement comprising a parallel connection of a damper and a spring is provided between the push mast and the vehicle frame or the displacement cylinder. It has been shown that such a damping arrangement significantly improves the operation of a reach truck.
  • Fig. 1 shows a mast 2 in the extended state. It has, for example, three mast sections to be extended and a fork-shaped load carrier 5, which is shown at the upper end of the extended mast and on which a load can be arranged. At the lower end of the mast 2, an adjusting cylinder 7 engages, through which the mast 2 can be moved in the direction of the double arrow 18.
  • the mast 2 can be moved back and forth in the direction of the double arrow 18 on a horizontal guide, namely on rollers 16, 17 and / or in corresponding rails.
  • the rollers 16, 17 only show the symmetrically movable support.
  • An arrangement 12 for damping vibrations occurring consists of a physical parallel arrangement with a spring 19 and a damper 20, which thus come into effect at the same time.
  • the arrangement 12 can be a self-contained unit, wherein springs can be selected and adjusted according to predetermined criteria and dampers are provided.
  • FIG. 2 shows a basic representation.
  • a point mass 11 acts on a mass-free intermediate piece 21 via a spring 22.
  • the arrangement 12 consists of the spring 19 and the damper 20. Both parts are supported on an abutment 23, which is the linkage 24 between the adjusting cylinder 7 and the arrangement 12 according to FIG. 1, for example. It is understood that the arrangement 12 is also connected to the mast 2 on the other hand via a joint 25.
  • FIG. 3 shows a basic overall arrangement of the hydraulic system for the adjustment of the mast 2, a special embodiment with a modification to FIG. 5 being dealt with in more detail.
  • adjusting cylinder 26 does not include the hydraulic jack drive that belongs to the mast. Only the adjusting cylinder is shown here as adjusting cylinder 26. A piston 27 is movably guided in it with a piston rod 28 led out through a cylinder end. This piston rod is, for example, as shown in FIG. 1, connected to the joint 24, which between the arrangement 12 and the adjusting cylinder is arranged.
  • the piston 27 divides the cylinder 26 into two cylinder spaces 29, 30. These cylinder spaces are connected near their ends to lines 31, 32 which are connected to a directional control valve 33. Between this directional valve 33, which can adjust a shut-off or an inflow in different directions in the usual way, and the adjusting cylinder 26, biasing valves 34 are arranged, which ensure the maintenance of a minimum pressure when they are arranged in the return. In the case of feeding, check valves 89, 90 connected in the preload valves open. The preload pressure is set so that a damping cylinder 35 can effectively dampen vibrations.
  • a piston 36 is guided in the damping cylinder 35, on which a piston rod 37 is arranged, the parts 26, 27; 28 are reproduced in the proportion.
  • the cylinder space 38 of the damping cylinder is connected to the cylinder space 29 of the adjusting cylinder 26, these two cylinder spaces being penetrated by the piston rods 28, 37.
  • the line 31 includes the cylinder space 38 and continues to the preload valve 34 and from there to the directional control valve 33.
  • a spring 71 is arranged inside the damping cylinder and on both sides of the piston, as is more clearly described with reference to FIG. 5.
  • the directional control valve 33 has two connections 40, 41 which are connected to a tank 39.
  • the first one contains a motor-driven pump 42.
  • the latter is the return line into the tank.
  • Both lines 31, 32 are connected to the tank 39 in parallel to the directional control valve 33 by means of derivatives 43, 44. Pressure relief valves 45, 46 are arranged in these derivatives.
  • the adjusting cylinder 26 can be driven in any direction by the directional control valve 33.
  • the damping cylinder 35 is connected to the lines 31, 32.
  • the cylinder space 47 on the side of the piston 36, which faces away from the piston rod 37, is connected by a connecting line 48 to the line 32 via a throttle section 49. This throttle section represents the damper.
  • an electrical solenoid valve 50 is arranged in the line 48, which via an electrical Control unit 51 is set to pass - as shown - or to lock. The latter is the case when the damping cylinder 35 is to be locked, so that the entire assembly is fixed. Such an adjustment is preferred if the stacking vehicle carries out longer journeys, in particular with the lifting frame retracted.
  • the directional control valve 33 When the adjusting cylinder 26 or its piston is extended for a specific setting of the mast, the directional control valve 33 is brought into the blocking position. Then the damping cylinder 35 and the throttle section 49 are connected via lines 31, 32 and the connecting line 48 to the adjusting cylinder 26, so that the damping becomes effective.
  • the adjusting cylinder 26 is connected in the manner shown. Therefore, the corresponding parts in FIGS. 4 to 6 are also designated with the same reference numerals.
  • a damping cylinder 52, 53 is connected to the lines 31, 32.
  • a row arrangement is physically present without being geometrically present.
  • only one damping cylinder 52 or 53 is arranged on one of the lines 31, 32.
  • the embodiment shown with two damping cylinders is preferred.
  • a piston 54, 55 is guided in both damping cylinders.
  • This piston is in each case held in a spring 56 which is arranged on both sides of the piston and supports this piston on the cylinder end walls.
  • the connections of the damping cylinders 52, 53 to the lines 31, 32 are designated 57, 58.
  • the electric solenoid valve 50 is arranged in the mouth of the connections 57, 58 in the damping cylinders 52, 53.
  • constricted passages 59, 60 are arranged as throttling sections or constricted bores, the constriction being designed such that it is closely related to the length in accordance with the above aspects.
  • the damper of the arrangement in which the flow energy is partly converted into heat and dissipated. It can be seen that this takes place simultaneously with the pressurization of the pistons 54, 55, so that both parts and thus also the spring 56 have a physically parallel effect.
  • the piston 27 moves in accordance with the pressure pulses occurring.
  • the hydraulic fluid is displaced on one side of the piston 27 and sucked in on the other side.
  • the hydraulic fluid must flow through the constricted passages 59, 60 or throttle sections.
  • Kinetic energy is converted into thermal energy and vibration damping is achieved.
  • the spring 56 also acts in the parallel arrangement.
  • FIG. 5 shows in more detail the damping cylinder 35 arranged in FIG. 3 within the framework of a hydraulic system that applies to all embodiments. This is connected at one end to the line 31 in the area of the cylinder chambers 29 and 38, which are penetrated by the piston rods 28 and 37 connected to the adjusting cylinder 26, the line connector being designated 67. The other end of the damping cylinder 35 is connected to the cylinder space 47 of the damping cylinder 35 by the line 32 or the connecting line 48, which contains the electric solenoid valve 50.
  • the damping cylinder 35 is divided into the two cylinder spaces 38 and 47 by a wall 68 with through openings 69, 70.
  • the piston 36 is guided in the cylinder space 38. However, it is held in a neutral position on both sides by a spring 71 corresponding to spring 56 in FIG. 4 and can be deflected from the neutral position against the spring.
  • the annular gap 72 is created as a throttle or annular passage in the cylinder space 47 in that an essentially cylindrical body 73 is arranged in it, the outer diameter of which is smaller than is the inner diameter of the damping cylinder 35.
  • the cylindrical body 73 is supported with end pieces 74, 75 and pins 76, 77 arranged on them in end wall parts, in an axial bearing a compression spring 78 is arranged, which brings about a tolerance.
  • FIG. 5 also shows, in comparison to FIG. 3, a throttle section (annular gap 72) 49 with respect to a damping piston 36 with a piston rod 37.
  • a throttle section annular gap 72
  • FIG. 5 which contains more details, in particular in connection with the spring 71, than FIG. 3, is subject to a special condition such that the dimensions for the arrangement with the actuating cylinder 26 and the parts with the damping cylinder 35 must be coordinated and chosen so that the area ratios of the pistons 27 and 36 with respect to the piston rods 28 and 37 are the same with respect to the cylinder spaces.
  • FIG. 6 shows the adjusting cylinder 26 with its piston 27, the piston rod 28 and the lines 31, 32 which connect this adjusting cylinder.
  • a damping cylinder is omitted.
  • hydraulic accumulators 79, 80 are connected to lines 31, 32 with pressure valves 34 by branch lines 81, 82.
  • Constricted passages 83, 84 are connected as throttling sections in these branch lines.
  • each hydraulic accumulators each contains a membrane 85, 86 which is supported on an enclosed and in this respect compressible gas volume 87, 88.
  • a piston rod 118 is provided, which guides a piston 119 within a cylinder 120. This is arranged on the piston rod so that it cannot be pivoted.
  • the piston 119 is guided with a seal in the cylinder.
  • the piston rod sections guided through the end faces of the cylinder 120 are sealed and, in a special embodiment, sealed in such a way that less canting is possible.
  • the cylinder 120 is mounted on the vehicle.
  • the piston rod 118 is connected to the mast via a joint 121 via an abutment 122.
  • the piston 119 is supported on both sides in the middle of the cylinder 120 within a spring 123. 7, the piston is penetrated by a constricted opening 124 which acts as a damping throttle.
  • the dimensioning corresponds to the viscosity of a liquid (oil) in the cylinder 120 and the forces or loads that occur. Leakage losses, for example due to worn sealing rings, are compensated for via an expansion tank 125 with an oil supply via a check valve 126.
  • a damping throttle 127 is arranged in a ring line 128 between the cylinder spaces on both sides of the piston.
  • a control valve 129 is additionally provided in the ring line as a solenoid valve, which switches the ring line to passage or blocking, the latter taking place when the mast is to be ascertained.
  • the cylinder spaces on both sides of the piston 119 are connected via connections 130, 131 to membrane stores 132, which replace the spring 123 in FIGS. 7 and 8 and in which flexible membranes 133, 134 are arranged in front of a compressible medium 135, 136.
  • Damping throttles 60 are located in the connections 130, 131 and a control valve 129 in one connection, as has already been described with reference to FIG. Only particularly preferred examples are shown here.

Landscapes

  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Structural Engineering (AREA)
  • Civil Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Mechanical Engineering (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • Vibration Prevention Devices (AREA)

Claims (15)

  1. Chariot élévateur, comportant un cadre de levage, sur lequel peut se déplacer en hauteur un support de charge (5), qui est monté mobile sur le chariot élévateur et sur lequel agit au moins un vérin de déplacement (7) à double effet destiné au déplacement de ce cadre de levage (2) et, dans la zone de la partie inférieure du cadre de levage (2), un dispositif amortisseur (12) élastique s'opposant aux oscillations,
       caractérisé en ce que le cadre de levage (2) est monté de façon à pouvoir coulisser sensiblement horizontalement, le vérin de déplacement (7) est, en conséquence, un vérin de coulissement, et le dispositif amortisseur (12) consiste en un ensemble agissant en parallèle, constitué d'un ressort (19; 56; 71; 85, 86) et d'au moins un amortisseur (20; 49; 52; 53; 60; 83; 84; 73), et agit dans les deux directions de déplacement du vérin de déplacement (7).
  2. Chariot élévateur suivant la revendication 1, caractérisé en ce que le dispositif amortisseur (12) est, pour son fonctionnement, disposé en série avec le vérin de déplacement (7).
  3. Chariot élévateur suivant la revendication 1 ou la revendication 2, caractérisé en ce que l'amortisseur (20) présente un passage à étranglement (49, 59, 60, 69, 70, 83, 84, 124, 139) pour le fluide de pression hydraulique du vérin de déplacement (7, 26).
  4. Chariot élévateur suivant l'une des revendications 1 à 3, caractérisé en ce que, pour le ressort (19, 116), la constante de rigidité élastique et, pour l'amortisseur hydraulique, la constante d'amortissement sont choisies telles qu'une oscillation s'annule progressivement après deux à trois oscillations.
  5. Chariot élévateur suivant l'une des revendications 1 à 4, caractérisé en ce que l'amortisseur (20) présente un dispositif cylindre-piston (35, 36, 52 à 55, 119, 120) dans lequel un piston travaille dans un cylindre, en agissant contre du fluide prisonnier dans ce cylindre.
  6. Chariot élévateur suivant la revendication 5, caractérisé en ce que le piston (54, 55) prend appui des deux côtés au moyen d'un ressort.
  7. Chariot élévateur suivant la revendication 5,
       caractérisé en ce que les deux extrémités du vérin de déplacement (26) sont reliées au vérin d'amortisseur (35),
       en ce que du côté d'une entrée du vérin d'amortisseur est disposé un élément de conduite à étranglement (49, 72) et du côté de l'autre entrée, est prévue une chambre de cylindre (38), pour le piston (36) cette chambre contient une tige de piston (37) sortante,
       en ce que le piston (36) est en appui élastique des deux côtés dans le cylindre amortisseur (35),
       et en ce que le rapport de la surface des pistons au diamètre de leur tige de piston (28, 37) est le même en ce qui concerne le piston (27) du vérin de déplacement (26), d'une part, et le piston (36) du vérin d'amortisseur (35), d'autre part.
  8. Chariot élévateur suivant la revendication 7, caractérisé en ce que le cylindre amortisseur (35) est divisé au moyen d'une paroi (68) présentant des ouvertures de passage (69, 70),
       que le piston (36), en appui élastique et comportant la tige de piston (37) qui sort, est disposé d'un côté de cette paroi,
       et qu'un corps intérieur (73), de dimensions extérieures plus faibles que le diamètre intérieur du vérin d'amortisseur (35) est disposé de l'autre côté de la paroi, une fente de passage (72) étant formée, sur le contour extérieur de ce corps, entre la conduite de raccordement (48) prévue à cette extrémité du vérin amortisseur (35) et la paroi (68).
  9. Chariot élévateur suivant l'une des revendications 1 à 4, caractérisé en ce que à chaque extrémité du vérin de déplacement (26) un raccord est relié à un accumulateur hydraulique (79, 80), dont les membranes (85, 86) forment les ressorts et dans le raccord duquel est disposé un passage à étranglement (83, 84).
  10. Chariot élévateur suivant l'une des revendications 1 à 9, caractérisé en ce que le cadre de levage (2) est monté dans des poutres latérales au-dessus d'une extrémité inférieure en étant guidé à la fois avec possibilité de pivoter (3) et également de se déplacer (91) dans le sens longitudinal du chariot, et en ce que le vérin de déplacement (7) est raccordé par articulation à son extrémité inférieure.
  11. Chariot élévateur suivant la revendication 10, caractérisé en ce que l'attaque du dispositif amortisseur (12) se fait dans la zone du palier de basculement (3).
  12. Chariot élévateur suivant la revendication 10 ou la revendication 11, caractérisé en ce que le dispositif amortisseur (12) présente un vérin amortisseur (120), dans lequel est guidé un piston (119), soumis des deux côtés à l'action d'un ressort et dont la tige de piston (118) sort à l'extérieur, en ce que le vérin amortisseur (120) est articulé sur un palier (122) solidaire du chariot, en pouvant pivoter par l'extrémité de la tige de piston sortant de l'autre côté, et en ce que le vérin (120) est divisé, par le piston (119), en deux chambres de cylindre (137, 138).
  13. Chariot élévateur suivant la revendication 12, caractérisé en ce que le piston (119) présente un passage (124) à étranglement, qui relie, par un étranglement, les deux chambres de vérin (137, 138).
  14. Chariot élévateur suivant la revendication 13, caractérisé en ce que les chambres de vérin (137, 138) situées des deux côtés du piston (119) sont reliées par une conduite annulaire (128), dans laquelle sont disposés un étranglement (127) et une soupape de commande (129) qui commute la conduite annulaire (128) en position d'ouverture ou de fermeture.
  15. Chariot élévateur suivant la revendications 12, caractérisé en ce que les deux chambres de cylindre (137, 138) sont reliées à des accumulateurs hydrauliques (132) comportant des membranes (133, 134), que l'un de ces accumulateurs (132) peut être coupé par une soupape de commande (129) et qu'un étranglement d'amortissement (139) est disposé dans au moins un raccord (130, 131) d'une chambre de vérin (137, 138).
EP90119648A 1989-11-10 1990-10-13 Chariot élévateur avec un mât de levage disposé mobilement Expired - Lifetime EP0427001B1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE3937404 1989-11-10
DE19893937404 DE3937404A1 (de) 1989-11-10 1989-11-10 Stapelfahrzeug mit einem beweglich an ihm angeordneten hubgeruest
DE9006695U 1990-06-15
DE4019075 1990-06-15
DE19904019075 DE4019075C2 (de) 1989-11-10 1990-06-15 Stapelfahrzeug mit einem Hubgerüst
DE9006695U DE9006695U1 (de) 1990-06-15 1990-06-15 Stapelfahrzeug mit einem Hubgerüst, an welchem ein Lastträger höhenbeweglich geführt ist

Publications (2)

Publication Number Publication Date
EP0427001A1 EP0427001A1 (fr) 1991-05-15
EP0427001B1 true EP0427001B1 (fr) 1996-02-07

Family

ID=27200430

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90119648A Expired - Lifetime EP0427001B1 (fr) 1989-11-10 1990-10-13 Chariot élévateur avec un mât de levage disposé mobilement

Country Status (2)

Country Link
EP (1) EP0427001B1 (fr)
DE (1) DE59010115D1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0840510A (ja) * 1994-08-01 1996-02-13 Murata Mach Ltd 昇降台吊持装置
GB2364992B (en) * 2000-07-24 2004-05-05 Lansing Linde Ltd Lifting structure for an industrial truck
GB2379434B (en) * 2001-09-10 2004-09-22 Lansing Linde Ltd Industrial truck with a lifting frame
DE102007015488A1 (de) * 2007-03-30 2008-10-02 Still Wagner Gmbh Schwingungskompensation am Hubgerüst eines Flurförderzeugs
CN114810883B (zh) * 2022-04-28 2024-04-26 中国舰船研究设计中心 一种双簧双侧并联支撑的推力轴承减振结构

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3321216A (en) * 1963-12-23 1967-05-23 Caterpillar Tractor Co Method and apparatus for controlling bounce in tractor-trailer combinations
US3480269A (en) * 1968-02-23 1969-11-25 Gates Rubber Co Hydraulic suspension unit
DE1913526B1 (de) * 1969-03-18 1970-09-03 Eaton Yale & Towne Gmbh Hublader mit zwei mittels Federn abgestuetzten vorderen Antriebsraedern
US3734326A (en) * 1971-07-15 1973-05-22 Eaton Corp Variable capacity lift truck
US3949892A (en) * 1974-11-29 1976-04-13 Caterpillar Tractor Co. Cushioned mast for lift trucks
DE2948605A1 (de) * 1979-12-03 1981-06-11 Ludwig Dr.-Ing. 7500 Karlsruhe Pietzsch Federsystem
FR2504905A1 (fr) * 1981-04-30 1982-11-05 Fenwick Manutention Ste Indle Chariot de manutention comportant un dispositif de suspension entre son chassis et son ensemble elevateur
DE3201917A1 (de) * 1982-01-22 1983-08-25 Josef 4802 Halle Kozlowski Sicherheitsvorrichtung fuer hubvorrichtungen
DE8908133U1 (de) * 1989-04-19 1989-08-31 Braun, Artur, 3523 Grebenstein Vorrichtung zur Abfederung und Dämpfung einer Fahrzeugkarosserie

Also Published As

Publication number Publication date
EP0427001A1 (fr) 1991-05-15
DE59010115D1 (de) 1996-03-21

Similar Documents

Publication Publication Date Title
DE69803839T2 (de) Doppeltwirkender dämpfer mit volumenausgleich für den hub der stange
EP0367949B1 (fr) Système de suspension pour véhicules
DE10122729A1 (de) Feder-Dämpfersystem für Fahrräder
DE112013004595B4 (de) Aufhängungsvorrichtung
EP1511642A1 (fr) Dispositif de suspension pour vehicules automobiles
EP1902221B1 (fr) Agencement piston-cylindre
DE3713997A1 (de) Fluidzylinder
DE4416228A1 (de) Hydraulische Anlage für ein mobiles Arbeitsgerät, insbesondere für einen Radlader
EP1709334A1 (fr) Accumulateur de pression, en particulier amortisseur de pulsations
DE3638574A1 (de) Anordnung zur drucksteuerung eines daempfungszylinders fuer die abfederung von fahrzeugen
DE2718962C2 (de) Gasfeder-Anordnung
DE112019002773T5 (de) Federungsvorrichtung
DE102006028878A1 (de) Hydraulische Stelleinheit für ein Kraftfahrzeug
DE102008013374A1 (de) Hydropneumatische Vorrichtung zur Druckübersetzung
EP0427001B1 (fr) Chariot élévateur avec un mât de levage disposé mobilement
EP0828942A1 (fr) Machine-outil hydropneumatique
DE4019075C2 (de) Stapelfahrzeug mit einem Hubgerüst
DE1296026B (de) Doppeltwirkender hydraulischer Teleskopschwingungsdaempfer, insbesondere fuer Kraftfahrzeuge
DE4212079A1 (de) Fluidendruckfeder und Konstruktion mit einer solchen Fluidendruckfeder
DE3937404C2 (fr)
EP1584502A1 (fr) Dispositif de suspension et d'amortissement pour véhicules motorisés
DE3345002A1 (de) Hydropneumatischer druckzylinder
DE3729187C2 (de) Verstellbare Dämpfung
DE102020119230A1 (de) Antriebsanordnung für eine Klappe eines Kraftfahrzeugs
EP3329142B1 (fr) Amortisseur de vibrations télescopique monotube hydraulique

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT SE

17P Request for examination filed

Effective date: 19910419

17Q First examination report despatched

Effective date: 19931222

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19960209

REF Corresponds to:

Ref document number: 59010115

Country of ref document: DE

Date of ref document: 19960321

ITF It: translation for a ep patent filed
ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19981203

Year of fee payment: 9

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20000801

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20081029

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20091023

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20091023

Year of fee payment: 20

Ref country code: FR

Payment date: 20091110

Year of fee payment: 20

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

Expiry date: 20101012

EUG Se: european patent has lapsed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20101012

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20091013