EP1085205B1 - Transmission hydraulique - Google Patents

Transmission hydraulique Download PDF

Info

Publication number
EP1085205B1
EP1085205B1 EP00120568A EP00120568A EP1085205B1 EP 1085205 B1 EP1085205 B1 EP 1085205B1 EP 00120568 A EP00120568 A EP 00120568A EP 00120568 A EP00120568 A EP 00120568A EP 1085205 B1 EP1085205 B1 EP 1085205B1
Authority
EP
European Patent Office
Prior art keywords
hydraulic
pressure
drive apparatus
distributor
distributor cylinder
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
EP00120568A
Other languages
German (de)
English (en)
Other versions
EP1085205A3 (fr
EP1085205A2 (fr
Inventor
Heinz Thumm
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP1085205A2 publication Critical patent/EP1085205A2/fr
Publication of EP1085205A3 publication Critical patent/EP1085205A3/fr
Application granted granted Critical
Publication of EP1085205B1 publication Critical patent/EP1085205B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0447—Controlling
    • F03C1/045—Controlling by using a valve in a system with several pump or motor chambers, wherein the flow path through the chambers can be changed, e.g. series-parallel

Definitions

  • the present invention relates to a hydraulic drive device, in particular a rotary device for excavator gripper and the like, with a stationary component and a moving component, in particular a stator and a rotor, at least two arranged between the fixed component and the moving component, at least partially separated hydraulic lines common hydraulic connections connectable pressure chambers which are alternately and successively pressurized with hydraulic fluid and thereby expandable and relieved and compressible via the hydraulic connections in such a way that moves the moving component relative to the stationary component, and a control device for controlling the supply and discharge of Hydraulic fluid in this way between the pressure chambers and the common hydraulic connections.
  • Such drive devices are known, for example, as axial or radial piston motors (see for example GB915231). But also vane motors and gear motors fall under this.
  • the invention has the object of providing a drive device of the type mentioned in such a way that these problems do not occur.
  • the drive device should be equipped with a braking device that is as light as possible and takes up little space.
  • the braking device should be as reliable as possible.
  • shut-off device is provided in a portion of the hydraulic line of at least one pressure chamber, which it does not share with the other pressure chambers, through which a drainage of hydraulic fluid from the pressure chamber is prevented.
  • a shut-off device is provided on at least two pressure chambers, which are pressurized in diametrically opposite phases. This ensures that the braking effect occurs regardless of the position of the moving component immediately. It is also possible to provide all pressure chambers with a shut-off device in order to further improve the braking effect.
  • the braking device according to the invention is basically used in all types of drive devices of the type mentioned, such as axial and radial piston drives, vane drives and gear drives.
  • the control device can also be designed in various ways, for example as a plan distributor or radial distributor. But also an electrical or electronic control device in conjunction with a path or angle measuring is possible. It is essential that the shut-off devices are arranged in the separate sections of the hydraulic lines of the pressure chambers, so that when closing the shut-off device, an exchange of hydraulic fluid between the individual pressure chambers is prevented.
  • the invention can be used both with endlessly rotatable drive devices and with drive devices which can only be rotated to a limited extent, and in principle also with translationally moved drive devices.
  • the shut-off device is automatically controlled in dependence on the operating state of the drive device. This ensures that the shut-off automatically opens upon actuation of the drive device and locks when stopping the drive device.
  • the shut-off device can be unlocked directly via the drive pressure of the hydraulic fluid. This can be done in a structurally inexpensive way a control of the shut-off device in dependence on the operating state of the drive device.
  • the pressure chambers are each formed as a piston pressure chamber of a piston-cylinder arrangement which is fixedly connected to one of the two elements, moving component and stationary component, and whose piston is supported via a rolling body on the other element.
  • a piston-cylinder arrangement which is fixedly connected to one of the two elements, moving component and stationary component, and whose piston is supported via a rolling body on the other element.
  • Such an arrangement is, for example, a radial piston drive or an axial piston drive, which have proven to be particularly advantageous as a rotating device for excavator grippers and the like.
  • a curved path is rotatably connected to the other element, on which run the rolling body of the piston.
  • the pistons are cyclically loaded in such an arrangement such that the piston and the curved path are continuously rotated in one direction relative to one another.
  • the curved path can be arranged on the rotor or on the stator. Accordingly, the pistons with the other element, ie stator or rotor, rotatably connected.
  • Such a configuration has the advantage that the rotor has a fixed axis of rotation.
  • the pistons are provided with sealing rings, in particular piston seals. This prevents that hydraulic fluid can escape through the annular gap between the piston and cylinder from the piston pressure chamber, so that a complete blockage of the drive device is made possible.
  • the control device is designed as a radial distributor, with a circular cross-section having distributor cylinder and a corresponding circular cylindrical manifold receptacle in which the distributor cylinder is rotatably guided, wherein the distributor cylinder with one of the two elements, stator and rotor, rotatably connected and the receptacle is arranged in the other element, and wherein the mutually separated sections of the hydraulic lines of the pressure chambers open into the manifold receptacle and alternately depending on the relative rotational position of the distributor cylinder and distributor receptacle on existing in the lateral surface of the distributor cylinder recesses and successively with a first annular groove provided in the distributor receptacle, which is connected to a first hydraulic connection, and a second, which is likewise seen in the receiving device Ring groove, which is connected to a second hydraulic connection, are connected.
  • the two hydraulic connections serve to supply and discharge of hydraulic fluid to the drive device
  • Distribution cylinder and distributor intake are such Device automatically rotated with the rotation of the rotor against each other and thereby control the supply and discharge of hydraulic fluid between the individual pressure chambers and the hydraulic connections via the opening into the manifold receiving individual hydraulic lines. The control is done in a cost effective and safe way.
  • the radial distributor is in the receptacle between a first position in which the portion of the hydraulic line at least one pressure chamber, which it does not have in common with the other pressure chambers, is closed, and a second position in which it is open , axially movable. Due to the axial displaceability of the radial distributor, the operation of the shut-off devices for braking the drive device can be realized in a simple manner.
  • the sections of the hydraulic lines are closed in the first position of the radial distributor by the lateral surface of the distributor cylinder, while they are connected in the second position via the recesses in the lateral surface with the first or the second annular groove.
  • the shut-off takes place in this embodiment so on the sliding fit of the distributor cylinder in the recording.
  • a further embodiment of the invention is in a portion of the hydraulic line at least one pressure chamber, this not with the other pressure chambers in common, each having a shut-off valve which is adjustable against the force of a return spring via a plunger in an open position, which plunger is guided in a recess opening into the receptacle of the radial distributor and is supported on the lateral surface of the distributor cylinder, wherein in the lateral surface is provided with an annular groove, in which the plunger engages in the first axial position of the distributor cylinder with its free end, so that the shut-off valve is closed, while the plunger is held in the open position in the second axial position of the distributor cylinder by its lateral surface.
  • shut-off valves By such shut-off valves a complete blockage of the hydraulic lines is possible.
  • a complete blocking of the rotating device can be achieved. Hydraulic fluid can not escape between the distributor cylinder and distributor intake, nor between the piston and cylinder from the pressure chambers of the blocked pistons.
  • the distributor cylinder has an axial Druckanstell structure to control its axial displacement.
  • the axial displacement of the distributor cylinder is thereby made possible in a simple manner.
  • the pressure contact surface of the distributor cylinder can be acted upon by drive pressure oil.
  • the distributor cylinder can be automatically moved axially upon actuation of the drive device and the braking device thereby be solved. External control is also possible.
  • an axially displaceable sleeve can also be provided, which comprises the distributor and locks the hydraulic lines opening into the receptacle in an axial position and releases them in the other axial position.
  • a particular advantage of the embodiment with axially displaceable distributor cylinder is also that the drive device can be constructed identical with and without brake device.
  • the distributor cylinder In the variant without braking device only the distributor cylinder must be correspondingly formed axially longer, or it must be provided a suitable spacer to prevent axial displacement of the distributor cylinder.
  • a pilot-operated check valve is arranged in a section of the hydraulic line at least one pressure chamber, which does not have this in common with the other pressure chambers.
  • the flow of hydraulic fluid through the hydraulic lines is thus not controlled via the distributor cylinder.
  • check valves are provided in the hydraulic lines, through which the pressure chambers are closed due to the existing hydraulic pressure there, when the check valves are not unlocked. This also makes complete blocking of the drive device possible.
  • the unlocking of the check valves is carried out according to a further embodiment of the invention preferably via the drive pressure oil. This again ensures that the braking device upon actuation of the drive device automatically resolved. External control is also possible.
  • a pressure limiting valve is arranged in at least one pressure chamber. This prevents damage to the drive device when too large a torque acts on the moving component when the drive device is locked.
  • a pressure relief valve is provided in all pressure chambers. As a result, damage to the drive device can be prevented particularly effectively.
  • the hydraulic drive device shown in Fig. 1 comprises a stator 1, which is connectable, for example, with an excavator boom, not shown, and a rotatably mounted on the stator about an axis I.
  • Rotor 2 on which, for example, a digging grab, also not shown, can be fastened.
  • stator 1 and rotor 2 can also be mounted vice versa, so that the stator 1 to the rotor and the rotor 2 to the stator.
  • the drive acting between stator 1 and rotor 2 comprises a plurality of piston-cylinder arrangements 3 arranged radially in relation to the axis of rotation I in the stator 1.
  • the cylinders of the piston-cylinder arrangements 3 are each formed by a recess 4 of circular cross-section in the stator 1 in which a piston 5 is displaceably guided in the radial direction. Between the radially inner base 6 of the recess 4 and the piston 5, a piston pressure chamber 7 is formed in each case. In this piston pressure chamber 7 each have a compression spring 8 is arranged, which is supported on the base 6 of the recess 4 and the piston 5 urges radially outward.
  • a roller-shaped rolling body 9 is provided in each case, which is rotatably mounted on the piston 5 about an axis II parallel to the axis II on the piston 5.
  • compression spring 8 of the rolling body 9 is urged against a cam track 10 which is provided on the rotor 2, the piston 5 opposite.
  • the distance of the cam track 10 from the rotation axis I changes cyclically around the rotation axis I between a maximum distance in which the piston 5 is extended, and a minimum distance in which the piston 5 is retracted.
  • the piston pressure chamber 7 of the piston-cylinder assemblies 3 is in each case via a hydraulic channel 11 with a provided in the stator 1 central recess 12 in connection whose free cross-section substantially the shape of a extending in the direction of the axis I circular cylinder has and which serves as a distributor receptacle.
  • a distributor cylinder 13 is also used with a substantially circular cross section, which is rotatably supported by the receptacle 12 about the rotation axis I and slidably guided between a first axial position and a second axial position.
  • the first axial position of the distributor cylinder 13 is determined by the bottom 14 of the receptacle 12, the second axial position by the rotor 2, which is rotatably connected to the stator 1 about the axis I.
  • the rotor 2 is rotatably connected to the stator 1 about the axis I.
  • About a engaging in an end-side recess 15 of the distributor cylinder 13 entrainment pin 16 of the distributor cylinder 13 is rotatably connected to the rotor 2.
  • a first annular groove 18 is introduced, which is connected via a hydraulic channel 19 with a first hydraulic connection 20. Furthermore, in the inner peripheral surface 17 of the receptacle 12, a second annular groove 21 is introduced, which is connected via a hydraulic passage 22 with a second hydraulic connection 23.
  • hydraulic connections 20 and 23 for example, coming from an excavator boom forth hydraulic lines are connected, which serve for the supply and discharge of hydraulic fluid.
  • About recesses 24 in the cylinder jacket surface 25 of the distributor cylinder 13 leading to the piston pressure chambers 7 hydraulic channels 11 are alternately connected in succession with one annular groove 18 and the other annular groove 21 in dependence on the rotational position of the distributor cylinder 13. In this way, the pressure chambers 7 are applied alternately with hydraulic pressure oil and relieved.
  • the piston 5 can retract radially into the recess 4 and the rolling body 9 on the curved path 10 uphill, so roll radially inward.
  • the rotor 2 continues to rotate in the same direction about the axis of rotation I.
  • the pressure chambers 7 of the other piston-cylinder assemblies 3 are alternately acted upon and relieved with hydraulic fluid, so that a continuous movement.
  • the distributor cylinder 13 has a pressure contact surface 26 which is directed transversely to the axis of rotation I and can be acted upon by drive pressure via an annular space 27 formed between distributor cylinder 13 and distributor receptacle 12, which can be connected to the hydraulic fluid supply via a hydraulic channel 28.
  • a changeover valve 29 ensures that the annular space 27 is acted upon by hydraulic fluid in both directions of rotation of the device.
  • the distributor cylinder 13 Upon application of the annular space 27 with hydraulic fluid, the distributor cylinder 13 is moved axially against the force of a restoring spring 30 in the direction of the rotor 2. Upon relief of Druckanstell procedure 26, the distributor cylinder 13 moves away under the force of the return spring 30 from the rotor 2 until the distributor cylinder 13 abuts the bottom 14 of the receptacle 12. This position is shown in Fig. 1. It remains between the distributor cylinder 13 and receptacle 12, a small annular space 27, via which the distributor cylinder 13 can be acted upon again with hydraulic fluid.
  • the recesses 24 While in the second position of the distributor cylinder 13, not shown here, the recesses 24 each connect an annular space 18 or 21 to the hydraulic channels 11 of the piston-cylinder assemblies 3, in the first axial position of the distributor cylinder 13 shown in FIG , Rather, the recesses 24 are connected only to the annular channel 18 or only to a hydraulic channel 11.
  • the annular groove 21 and a part of the hydraulic channels 11, however, is closed by the lateral surface 25 of the distributor cylinder 13.
  • no hydraulic fluid can flow out of the piston pressure chambers 7. It only occurs a certain leakage between distributor cylinder 13 and receptacle 12. However, the rotor is braked against rotation relative to the stator 1, since the pistons 5 can not or only very slowly enter the recesses 4 according to the amount of leakage.
  • one piston piston 5 is in each case connected to the piston pressure chamber 7 connected and in the low pressure space 31 between the rotor 2 and stator 1 opening pressure relief valve 32 is provided.
  • a shut-off valve 33 is arranged in the hydraulic channels 11 between the piston pressure chamber 7 and receptacle 12, which is displaceable via a plunger 34 against the force of a return spring 35 in the open position.
  • the plunger 34 is guided in a recess 36 between the hydraulic channel 11 and receptacle 12 and is supported by its free end 37 on the cylinder jacket surface 25 of the distributor cylinder 13 from.
  • an annular groove 38 is introduced, in which the plunger 34 can retract with its free end 37 when the distributor cylinder 13 is in its position remote from the rotor 2.
  • the drive basically agrees with the two previous variants.
  • the distributor cylinder 13 is not axially displaceable here.
  • a pilot-operated check valve 39 is arranged in the hydraulic lines 11 between the piston pressure chambers 7 and the receptacle 12, through which the piston pressure chambers 7 are completely shut off.
  • the first variant of the drive device according to the invention acts as a brake
  • the second and third variants lead to a blocking of the drive device.
  • one or the other variant can be selected.
  • the brake or Blokkier worn is structurally inexpensive, little space consuming and light. In addition, it is reliable. In particular, no functional impairment occurs due to contamination and wear.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Actuator (AREA)
  • Component Parts Of Construction Machinery (AREA)
  • Valve Device For Special Equipments (AREA)
  • Hydraulic Motors (AREA)

Claims (12)

  1. Dispositif d'entraînement hydraulique, en particulier dispositif rotatif pour pelle preneuse-excavatrice et similaire, comprenant un composant stationnaire (1) et un composant mobile (2), en particulier un stator (1) et un rotor (2), au moins deux chambres de pression (7) agencées entre le composant stationnaire (1) et le composant mobile (2) et susceptibles d'être reliées à des raccords hydrauliques communs (20, 23) via des conduites hydrauliques (11, 19, 22) séparées l'une de l'autre au moins par tronçons, lesdites deux chambres pouvant être alimentées en pression via les raccords hydrauliques (20, 23) en alternance et en succession avec un liquide hydraulique et de ce fait mises en expansion ou déchargées et ainsi comprimées, de telle façon que le composant mobile (2) se déplace par rapport au composant stationnaire (1), et comprenant une unité de commande pour commander l'admission et l'évacuation du liquide hydraulique de cette façon entre les chambres de pression (7) et les raccords hydrauliques communs (20, 23), dans lequel dans un tronçon (11) de la conduite hydraulique de l'une au moins un des chambres de pression (7), que celle-ci ne possède pas en commun avec l'autre chambre de pression (7), il est prévu un agencement de blocage (33, 39),
    caractérisé en ce que
    au moyen de l'agencement de blocage (33, 39) un écoulement du liquide hydraulique hors de la chambre de pression (7) est empêché.
  2. Dispositif d'entraînement selon la revendication 1,
    caractérisé en ce que l'agencement de blocage (33, 39) peut être commandé automatiquement en fonction de l'état de fonctionnement du dispositif d'entraînement, ledit agencement de blocage (33, 39) pouvant être débloqué en particulier directement via la pression d'entraînement du liquide hydraulique.
  3. Dispositif d'entraînement selon l'une des revendications précédentes,
    caractérisé en ce que les chambres de pression (7) sont respectivement réalisées sous forme d'une chambre à pression d'un agencement à piston-et-cylindre (3) qui est fermement relié à l'un des deux éléments que sont le composant stationnaire (1) et le composant mobile (2), et dont le piston (5) s'appuie contre l'autre élément via un corps à roulements (9).
  4. Dispositif d'entraînement selon la revendication 3,
    caractérisé en ce qu'il est réalisé sous forme de dispositif rotatif avec stator (1) et rotor (2), et en ce qu'à l'autre élément est reliée solidairement en rotation une voie incurvée (10) sur laquelle circulent les corps de roulement (9) des pistons (5).
  5. Dispositif d'entraînement selon la revendication 3 ou 4,
    caractérisé en ce que les pistons (5) sont pourvus de bagues d'étanchéité, en particulier de joints à pistons.
  6. Dispositif d'entraînement selon l'une des revendications précédentes,
    caractérisé en ce qu'il est réalisé sous forme de dispositif rotatif avec stator (1) et rotor (2), et en ce que le système de commande est réalisé sous forme de distributeur radial avec un cylindre distributeur (13) présentant une section circulaire et un logement (12) cylindrique correspondant dans lequel le cylindre distributeur (13) est guidé avec possibilité de rotation, ledit cylindre distributeur (13) étant relié solidairement en rotation à l'un des deux éléments que sont le stator (1) et le rotor (2), et le logement (12) est prévu dans l'autre élément, et dans lequel les tronçons (11), séparés l'un de l'autre, des conduites hydrauliques des chambres de pression (7) débouchent dans le logement (12) et, en fonction de la position de rotation relative du cylindre distributeur (13) et du logement (12), celles-ci sont reliées via des évidements (24) prévus dans la surface enveloppe (25) du cylindre distributeurs (13), alternativement et les unes après les autres, à une première gorge annulaire (18) prévue dans le logement (12) et raccordée à un premier raccord hydraulique (20), et à une seconde gorge annulaire (21) prévue également dans le logement (12) et raccordée à un second raccord hydraulique (23).
  7. Dispositif d'entraînement selon la revendication 6,
    caractérisé en ce que le cylindre distributeur (13) est susceptible d'être déplacé axialement dans le logement (12) entre une première position, dans laquelle un tronçon (11) de la conduite hydraulique de l'une au moins des chambres de pression (7) que celle-ci ne possède pas en commun avec les autres chambres de pression (7), est fermé, et une seconde position, dans laquelle celui-ci est ouvert.
  8. Dispositif d'entraînement selon la revendication 7,
    caractérisé en ce que, dans la première position, les tronçons (11) des conduites hydrauliques sont fermés par la surface enveloppe (25) du cylindre distributeur (13), tandis que, dans la seconde position, ils sont reliés via les évidements (24) dans la surface enveloppe (25) du cylindre distributeur (13) respectivement soit à la première gorge annulaire (18) soit à la seconde gorge annulaire (21).
  9. Dispositif d'entraînement selon la revendication 7,
    caractérisé en ce que, dans un tronçon (11) de la conduite hydraulique de l'une au moins des chambres de pression (7), que celle-ci ne possède pas en commun avec les autres chambres de pression (7), est agencé un clapet de fermeture (33) qui peut être amené à l'encontre de la force d'un ressort de rappel (35) au moyen d'un poussoir (34) jusque dans une position ouverte, ledit poussoir (34) étant guidé dans un évidement (36) qui débouche dans le logement (12) du distributeur radial et étant soutenu sur la surface enveloppe (25) du cylindre distributeur (13), et il est prévu dans la surface enveloppe (25) une gorge annulaire (38) dans laquelle le poussoir (34) est susceptible d'entrer par son extrémité libre (37), dans la première position axiale du cylindre distributeur (13), de sorte que le clapet de fermeture (33) est fermé, alors que le poussoir (34) est maintenu en position ouverte par la surface enveloppe (25) du cylindre distributeur (13) dans la seconde position axiale de celui-ci.
  10. Dispositif d'entraînement selon l'une des revendications 7 à 9,
    caractérisé en ce que le cylindre distributeur (13) présente une surface d'application de pression (26) pour la commande de son déplacement axial, ladite surface d'application de pression (26) étant de préférence soumise à la pression d'une huile motrice.
  11. Dispositif d'entraînement selon l'une des revendications 1 à 6,
    caractérisé en ce que, dans un tronçon (11) des conduites hydrauliques de l'une au moins des chambres de pression (7), que celle-ci ne possède pas en commun avec les autres chambres de pression (7), est agencé un clapet antiretour (39) respectif déblocable, lesdits clapets antiretour (39) pouvant être débloqués de préférence via la pression de l'huile motrice.
  12. Dispositif d'entraînement selon l'une des revendications précédentes,
    caractérisé en ce que dans l'une au moins des chambres de pression (7) est agencé un clapet de limitation de pression (31) qui s'ouvre dans une chambre à basse pression (31) du dispositif d'entraînement.
EP00120568A 1999-09-20 2000-09-20 Transmission hydraulique Expired - Lifetime EP1085205B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19944987 1999-09-20
DE19944987A DE19944987A1 (de) 1999-09-20 1999-09-20 Hydraulische Antriebsvorrichtung

Publications (3)

Publication Number Publication Date
EP1085205A2 EP1085205A2 (fr) 2001-03-21
EP1085205A3 EP1085205A3 (fr) 2003-01-15
EP1085205B1 true EP1085205B1 (fr) 2007-05-23

Family

ID=7922627

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00120568A Expired - Lifetime EP1085205B1 (fr) 1999-09-20 2000-09-20 Transmission hydraulique

Country Status (3)

Country Link
EP (1) EP1085205B1 (fr)
AT (1) ATE363026T1 (fr)
DE (2) DE19944987A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10300265A1 (de) * 2003-01-08 2004-07-22 Heinz Thumm Ölhydraulische Antriebe GmbH Drehvorrichtung für Lastaufnahmemittel wie Baggergreifer und dergleichen
DE10309258B4 (de) * 2003-03-03 2006-10-12 Archimedes Voulgaris Hydraulikmotorenbau Gmbh Einrichtung zur Befestigung und zum Drehantrieb eines Greiferwerkzeugs
DE102009060452B4 (de) 2009-12-24 2016-12-29 Thyssenkrupp Rothe Erde Gmbh Druckmittelbetätigter Drehantrieb

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1249873A (fr) * 1959-11-13 1961-01-06 Poclain Bataille Et Fils Atel Moteur hydraulique perfectionné
DE2838346C2 (de) * 1978-09-02 1985-02-14 Fa. Heinz Thumm, 7012 Fellbach Drehvorrichtung für einen Baggergreifer o.dgl.
DE3109706C2 (de) * 1981-03-13 1986-09-18 G. Düsterloh GmbH, 4322 Sprockhövel Volumenschaltbarer Hydromotor
FR2706538B1 (fr) * 1993-06-09 1995-09-01 Poclain Hydraulics Sa Mécanisme à fluide sous pression tel qu'un moteur ou une pompe, réversible, à au moins deux cylindrées de fonctionnement.

Also Published As

Publication number Publication date
DE50014341D1 (de) 2007-07-05
DE19944987A1 (de) 2001-03-22
EP1085205A3 (fr) 2003-01-15
ATE363026T1 (de) 2007-06-15
EP1085205A2 (fr) 2001-03-21

Similar Documents

Publication Publication Date Title
AT511833B1 (de) Mastaufbau insbesondere für eine autobetonpumpe
EP1025343A1 (fr) Dispositif de modification relative de la position en rotation d'un arbre par rapport au pignon d'entree
DE1729156B1 (de) Formschliesseinrichtung fuer spritzgiessmaschinen
EP2570680B1 (fr) Procédé de déverrouillage d'un cylindre de verrouillage
DE2004097A1 (de) Vorrichtung an Luftfahrzeugen zur Steuerung eines Fahrwerks und seiner Abdecktuer
EP1085205B1 (fr) Transmission hydraulique
WO2005017366A1 (fr) Verin
DE2137537C3 (de) Steuerung für einen hydrostatischen Kolbenmotor
EP3344881B1 (fr) Vérin de blocage hydromécanique et système de commande hydraulique pour l'actionner
EP0809736B1 (fr) Mecanisme vireur pour benne preneuse
DE10044784A1 (de) Verstellvorrichtung für eine Axialkolbenmaschine in Schrägachsenbauweise
EP0505349B2 (fr) Vérin hydraulique
DE68905659T2 (de) Hydraulischer radialkolbenmotor mit veraenderbarem hubvolumen.
DE2552677B2 (de) Hydrostatische Radialkolbenmaschine
DE10356598B3 (de) Verriegelungszylinder
EP1170512B1 (fr) Vérin à fluide sous pression avec verrouillage mécanique lorsque non pressurisé
DE10356596B3 (de) Verriegelungszylinder
EP0058878B1 (fr) Appareil pour la rotation de charges suspendues
EP1437323B1 (fr) Dispositif de rotation pour moyens de prise de charge comme des grapins d'excavatrice
EP0089568B1 (fr) Dispositif d'actionnement rotatif à fluide sous pression
DE10356597B3 (de) Verriegelungszylinder
EP0735233B1 (fr) Obturateur à manchon actionné hydrauliquement pour puits
DE2450330B2 (de) Doppelhydraulischer stellantrieb
DE2318880A1 (de) Ventil mit stillegungsvorrichtung
DE102015116024A1 (de) Schwenkmotorversteller einer Nockenwelle

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: A2

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

17P Request for examination filed

Effective date: 20030715

AKX Designation fees paid

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE

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

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070523

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REF Corresponds to:

Ref document number: 50014341

Country of ref document: DE

Date of ref document: 20070705

Kind code of ref document: P

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

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070903

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
GBV Gb: ep patent (uk) treated as always having been void in accordance with gb section 77(7)/1977 [no translation filed]

Effective date: 20070523

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

EN Fr: translation not filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070523

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070523

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071023

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070523

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

BERE Be: lapsed

Owner name: THUMM, HEINZ

Effective date: 20070930

26N No opposition filed

Effective date: 20080226

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

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070523

Ref country code: GB

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070523

Ref country code: MC

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

Effective date: 20070930

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070824

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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

Ref country code: FR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080118

Ref country code: LI

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

Effective date: 20070930

Ref country code: CH

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

Effective date: 20070930

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

Ref country code: BE

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

Effective date: 20070930

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

Ref country code: AT

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

Effective date: 20070920

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

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070523

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

Ref country code: LU

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

Effective date: 20070920

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

Ref country code: SE

Payment date: 20190927

Year of fee payment: 20

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

Ref country code: DE

Payment date: 20191129

Year of fee payment: 20

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 50014341

Country of ref document: DE