EP2024666A1 - Mecanisme d'entrainement hydrostatique comprenant un circuit hydraulique ouvert et un circuit hydraulique ferme - Google Patents

Mecanisme d'entrainement hydrostatique comprenant un circuit hydraulique ouvert et un circuit hydraulique ferme

Info

Publication number
EP2024666A1
EP2024666A1 EP07725764A EP07725764A EP2024666A1 EP 2024666 A1 EP2024666 A1 EP 2024666A1 EP 07725764 A EP07725764 A EP 07725764A EP 07725764 A EP07725764 A EP 07725764A EP 2024666 A1 EP2024666 A1 EP 2024666A1
Authority
EP
European Patent Office
Prior art keywords
circuit
hydraulic
working
hydrostatic drive
closed
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.)
Withdrawn
Application number
EP07725764A
Other languages
German (de)
English (en)
Inventor
Seppo Tikkanen
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.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik 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 Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP2024666A1 publication Critical patent/EP2024666A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/4078—Fluid exchange between hydrostatic circuits and external sources or consumers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/4148—Open loop circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
    • F16H61/421—Motor capacity control by electro-hydraulic control means, e.g. using solenoid valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2200/00—Type of vehicle
    • B60Y2200/40—Special vehicles
    • B60Y2200/41—Construction vehicles, e.g. graders, excavators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/42—Control of exclusively fluid gearing hydrostatic involving adjustment of a pump or motor with adjustable output or capacity
    • F16H61/431—Pump capacity control by electro-hydraulic control means, e.g. using solenoid valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/44—Control of exclusively fluid gearing hydrostatic with more than one pump or motor in operation
    • F16H61/444—Control of exclusively fluid gearing hydrostatic with more than one pump or motor in operation by changing the number of pump or motor units in operation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/38—Control of exclusively fluid gearing
    • F16H61/40—Control of exclusively fluid gearing hydrostatic
    • F16H61/44—Control of exclusively fluid gearing hydrostatic with more than one pump or motor in operation
    • F16H61/448—Control circuits for tandem pumps or motors

Definitions

  • the invention relates to a hydrostatic drive with an open hydraulic circuit and a closed hydraulic circuit.
  • the vehicle is the closed hydraulic circuit is not used, while in the open hydraulic circuit several hydraulic consumers can be active simultaneously. This requires a considerable dimensioning of the arranged in the open circuit hydraulic pump. This not only leads to a high investment but is also uneconomical in the operation of the vehicle.
  • the invention is therefore an object of the invention to provide a hydrostatic drive with an open circuit and a closed circuit, which is improved in terms of its efficiency.
  • the hydrostatic drive according to the invention comprises an open hydraulic circuit and a closed one hydraulic circuit.
  • the closed hydraulic circuit has at least one working circuit and one driving circuit.
  • the open hydraulic circuit is connected to at least one hydraulic consumer of a working hydraulics. In this way, when the vehicle is at a standstill, the working hydraulics comprising a plurality of hydraulic consumers are connected for actuation both to an open circuit hydraulic pump and to a closed loop hydraulic pump.
  • the working hydraulics has individual hydraulic consumers. There is an allocation of a part of these hydraulic consumers to the hydraulic pump of the open circuit. In contrast, at least one further hydraulic consumer of the working hydraulics is connected to the closed circuit in a working cycle. This is particularly advantageous because usually both the open circuit and the closed circuit are driven by a common drive machine. In this case, both hydraulic pumps are usually connected to the prime mover at the same time. Upon actuation of the working hydraulics, therefore, the hydraulic pump of the drive hydraulics is also driven anyway.
  • the inventive division of the hydraulic load of the working hydraulics on the open circuit and the closed circuit the losses are minimized and at the same time it is possible to make the pump in the hydraulic circuit in terms of their performance smaller. The weight savings achieved thereby leads, in addition to a reduction in the original investment, to a reduction in fuel consumption during driving, since the total mass of the vehicle is reduced.
  • valve device in the closed hydraulic circuit, by means of which it is possible to switch between the working cycle and the travel cycle.
  • valve device thus in each case a closed hydraulic partial circuit is formed, in which the hydraulic pump is arranged.
  • the currently not required second circuit part is decoupled. Uncoupling the drive circuit thus ensures that accidental driving of the drive wheels is prevented.
  • the working cycle can contain allocation valves with which several consumer line branches can be assigned to the respective suction or pressure-side working lines of the closed circuit.
  • the valve block may also have a load-holding valve and / or a pressure-limiting valve. Since the valve block is assigned to the working cycle, regardless of possibly already existing pressure limiting valves to secure the closed circuit, a hedge of the working cycle and in particular of the hydraulic consumer itself can be done.
  • a purge valve is additionally provided in the valve block.
  • the hydraulic pumps of the open circuit and the closed circuit are mechanically interconnected according to a further preferred embodiment, so that a rigid coupling between the two pumps is possible.
  • This has the particular advantage that at a most oppressive load in the further hydraulic consumer a
  • the hydraulic pump of the closed circuit is adjustable in its delivery volume and designed to convey pressure medium in two directions.
  • the control of the further hydraulic consumer takes place by adjusting the conveying direction and the required flow rate.
  • Complex control via reducing valves and adjustable throttles can thus be dispensed with.
  • the combination with a lifting cylinder is provided as a further hydraulic consumer.
  • Fig. 1 is a schematic representation of the hydrostatic drive according to the invention.
  • the hydrostatic drive 1 comprises an open circuit 2 and a closed circuit 3.
  • a hydraulic pump unit 4 is provided which has an adjustable hydraulic pump 5.
  • the adjustable hydraulic pump 5 is coupled to a feed pump 6 to the hydraulic pump unit 4.
  • the hydraulic pump 5 is provided for generating a delivery flow in the closed hydraulic circuit 3 and connected to a first working line 7 and a second working line 8.
  • the hydraulic pump 5 is designed for conveying in both directions.
  • Circuit 3 comprises in addition to the hydraulic pump 5, the first working line 7 'and the second working line 8', a hydraulic motor 9.
  • the hydraulic motor 9 is adjustable in the illustrated embodiment in its displacement and a first working line section 7 'and a second working line section 8' with the first Working line 7 and the second working line 8 and thus connected to the hydraulic pump 5.
  • the hydraulic motor 9 is connected via an output shaft 10 with a differential gear 11.
  • the differential gear 11 is, for example, a rear axle of a mobile machine.
  • the torque applied to the differential gear 11 acts on a first half-wave 12 and a second half-wave 13 on a first and a second drive wheel 14, 15th
  • connection of the hydraulic motor 9 with the hydraulic pump 5 takes place via a first
  • a further hydraulic pump 17 is provided, which is arranged in the open circuit 2.
  • the further hydraulic pump 17 is also in her Volume adjustable, but only designed for conveying in one direction.
  • a working hydraulic 18 is actuated by the entire hydrostatic drive 1.
  • the working hydraulics; 18 includes in the illustrated embodiment, a first hydraulic cylinder 20, a second hydraulic cylinder 21 and a third hydraulic cylinder 23.
  • the first and second hydraulic cylinders 20, 21 are acted upon by the further hydraulic pump 17 of the open hydraulic circuit 2 with pressure medium.
  • the third hydraulic cylinder 23 is, however, associated with the closed hydraulic circuit 3 and is coupled to the hydraulic pump 5 via the valve block 16, provided that the closed hydraulic circuit 3 is not required for the traction drive.
  • the first hydraulic cylinder 20 is designed in the illustrated embodiment as a double-acting lifting cylinder, wherein in the first hydraulic cylinder 20, a piston 24 is arranged, which divides the first hydraulic cylinder 20 into a piston surface space 27 and a piston rod space 28.
  • a second piston 25 is provided in the second hydraulic cylinder 21, which in turn subdivides the second hydraulic cylinder 21 into a piston surface space 29 and a piston rod space 30.
  • the closed hydraulic circuit 3 associated third hydraulic cylinder 23 has in a corresponding manner to a piston 26 which is arranged longitudinally displaceable in the third hydraulic cylinder 23.
  • the hydraulic cylinder 23 is also divided into a piston surface space 31 and a piston rod chamber 32.
  • the pistons 24, 25 and 26 are respectively on the side of the
  • Piston surface space 27, 29 and 31 and on the oriented in the opposite direction surface in the piston rod chamber 28, 30, 32 acted upon by a control pressure.
  • the signal pressure for the first Working cylinder 20 and the second working cylinder 21 through the open hydraulic circuit 2 and the arranged therein further hydraulic pump 17 is generated.
  • pressure is generated by the hydraulic pump 5. Because of the
  • the closed hydraulic circuit 3 is formed alternately by a drive circuit 36 or a working circuit 37.
  • the components of the circulation circuit 36 have already been discussed, which comprises the first working line branch 7 ', the hydraulic pump 9 and the second working line branch 8'.
  • the circulation circuit 36 together with the first working line 7 and the second working line 8 and the hydraulic motor 5, the closed hydraulic circuit 3 when a driving operation is required.
  • the working cycle 37 comprises in addition to the third
  • Hydraulic cylinder 23 a first consumer line 38 and a second consumer line 39, which are connected via the valve means of the valve block 16 with the first working line 7 and the second working line 8. If the vehicle is stationary, it is possible to switch between the working circuit 37 and the travel circuit 36.
  • a first switching valve 40 and a second switching valve 41 which form the valve device, are preferably arranged in the valve block 16 for this purpose.
  • Switching valve 41 are connected to each other via a coupling rod 42, so that a common operation is possible.
  • the first switching valve 40 and the second switching valve 41st the first working line 7 is connected to the first working line section 7 '.
  • the second working line 8 is connected to the second working line section 8 '.
  • an electromagnetic actuation is provided on the first switching valve 40.
  • the first switching valve 40 is acted upon by an electromagnet 43 in the direction of its second switching position. The movement that the
  • Solenoid 40 generated in the first switching valve 40 is transmitted via the coupling rod 42 to the second switching valve 42, which is consequently also moved to its second switching position.
  • the movement on the first switching valve 40 and the second switching valve 41 is performed against a compression spring 44 provided on the second switching valve 42. If the electromagnet 43 is no longer energized, so the second switching valve 41 and consequently the first switching valve 40 is again in its first by the compression spring 44
  • the first switching valve 40 and the second switching valve 41 are provided in the illustrated embodiment alone to between the travel circuit 36 and the
  • the activation of the electromagnet 43 can therefore be advantageously coupled to an idling sensor, for example.
  • the allocation valve block 48 connects to the assignment of the piston rod chamber 32 and the piston surface space 31 to the first working line 7 or to the second working line 8 either a first Bistechnischszweig 38 'with the first consumer line 38 and at the same time a second Cir effetszweig 39' with the second consumer line 39 or the first Self effetszweig 38 'with the second consumer line 39 and the second consumer line branch 39 'with the first consumer line 38.
  • the assignment valve block 28 can preferably also be realized with simple switching valves.
  • the positioning speed and adjusting direction is determined by adjusting the variable hydraulic pump 5.
  • the open hydraulic circuit 2 comprises, in addition to the further hydraulic pump 17, a suction line 49.
  • the further hydraulic pump 17 sucks in pressure medium via the suction line 49 from a tank volume 50 and delivers it to a delivery line 51.
  • the delivery line 51 can be connected by a first control valve unit 52 to a first connection line 54 or a second connection line 55.
  • a supply of pressure medium from the delivery line 51 into the piston surface space 29 or the piston rod space 30 of the second hydraulic cylinder 21 is possible via a third connecting line 56 or a fourth connecting line 57.
  • connection of the third connection line 56 and the fourth connection line 57 to the delivery line 51 via a second valve unit 53 The first valve unit 52 and the second valve unit 53 are preferably integrated in a common housing. Instead of a connection of the delivery line 51 with one of the connecting lines 54 to 57, a connection to an expansion line 57 can be produced by the valve units 52, 53. If, for example, a stroke movement of the piston 24 of the first hydraulic cylinder 20 is to be performed by pressing the piston surface space 27, the first connection unit 54 connects the first connection unit 54 to the delivery line 51. At the same time, in order to enable a volume compensation, the second connecting line 55 of the piston rod chamber 28 is connected to the expansion line 57. The displaced from the piston rod chamber 28 pressure fluid is thus discharged into the tank volume 50.
  • the actuation of the second hydraulic cylinder 21 takes place in the same way, so that it can be dispensed with a new description.
  • the first valve unit 52 and the second valve unit 53 can be actuated together or separately from one another and are connected to the delivery line 51 and the expansion line 57 via common connections.
  • a common drive motor 45 which is coupled via a drive shaft 46 with the hydraulic pumps 5, 6, 17.
  • a feed pump 6 is provided in the hydraulic pump unit 4 in addition to the hydraulic pump 5.
  • the feed pump 6 sucks on a feed pump suction 58 also from the tank volume 50 pressure medium and promotes it via a
  • Supply pressure line 59 in a not shown feed pressure system.
  • any other hydraulic consumer can be used.
  • the individual hydraulic consumers of the working hydraulics 18 do not have to have the same embodiment.
  • a hydraulic cylinder which usually is only pressurized to provide 3 in the closed hydraulic circuit.
  • the weight which presses on the piston rod 35 generates in the piston surface space 31 a pressure which is supplied via the second consumer line branch 39 'and the valve block 16 of the hydraulic pump 5 and is supported there.
  • the hydraulic pump 5 acts as a hydraulic motor and generates a torque which is supplied via the drive shaft 46 of the further hydraulic pump 17.
  • the common drive machine 45 thus only needs to generate a reduced torque for driving the further hydraulic pump 17, whereby the fuel consumption of the drive motor 45 decreases.
  • a load-holding valve is preferably arranged in the allocation valve block 48, which connects between the first and second consumer line branch 38 ', 39' and the first consumer line 38 and the second consumer line 39 interrupts.
  • a flushing valve can preferably also be integrated in the common valve block 16, which in particular contains all the valves required for operating the circulation circuit 36 and the working cycle 37.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un mécanisme d'entraînement hydrostatique comprenant un circuit (2) hydraulique ouvert et un circuit (3) hydraulique fermé. Au moins une charge (20, 21) hydraulique d'un équipement (18) hydraulique de travail est disposée dans le circuit (2) hydraulique ouvert. Le circuit (3) hydraulique fermé comprend un circuit (37) de travail et un circuit (36) de déplacement, au moins une charge (23) hydraulique supplémentaire étant disposée dans le circuit (37) de travail.
EP07725764A 2006-06-02 2007-06-01 Mecanisme d'entrainement hydrostatique comprenant un circuit hydraulique ouvert et un circuit hydraulique ferme Withdrawn EP2024666A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200610025985 DE102006025985A1 (de) 2006-06-02 2006-06-02 Hydrostatischer Antrieb mit einem offenen hydraulischen Kreislauf und einem geschlossenen hydraulischen Kreislauf
PCT/EP2007/004884 WO2007140945A1 (fr) 2006-06-02 2007-06-01 Mécanisme d'entraînement hydrostatique comprenant un circuit hydraulique ouvert et un circuit hydraulique fermé

Publications (1)

Publication Number Publication Date
EP2024666A1 true EP2024666A1 (fr) 2009-02-18

Family

ID=38370390

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07725764A Withdrawn EP2024666A1 (fr) 2006-06-02 2007-06-01 Mecanisme d'entrainement hydrostatique comprenant un circuit hydraulique ouvert et un circuit hydraulique ferme

Country Status (4)

Country Link
EP (1) EP2024666A1 (fr)
CA (1) CA2625203A1 (fr)
DE (1) DE102006025985A1 (fr)
WO (1) WO2007140945A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015121782A1 (de) * 2015-12-15 2017-06-22 Linde Hydraulics Gmbh & Co. Kg Mobile Arbeitsmaschine mit einem hydrostatischen Fahrantrieb und einer Arbeitshydraulikpumpe

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ATE26234T1 (de) * 1983-09-15 1987-04-15 Zahnradfabrik Friedrichshafen Hydrostatisch-mechanische getriebeanordnung.
US4754603A (en) * 1987-07-20 1988-07-05 Rosman Allan H Hydraulic-drive system for an intermittent-demand load
DE19751001A1 (de) * 1997-11-18 1999-05-20 Zahnradfabrik Friedrichshafen Verfahren und Vorrichtung zur Verhinderung der Zugkraftunterbrechung beim Zu- und Abschalten von Hydromotoren
US6601474B2 (en) * 2000-09-05 2003-08-05 Kanzaki Kokyukoki Mfg. Co., Ltd. Hydrostatic transmission and power train for vehicle
DE102004044510A1 (de) * 2004-09-15 2006-03-30 Zf Friedrichshafen Ag Hydraulisches Getriebe

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2007140945A1 *

Also Published As

Publication number Publication date
WO2007140945A1 (fr) 2007-12-13
DE102006025985A1 (de) 2007-12-06
CA2625203A1 (fr) 2007-12-13

Similar Documents

Publication Publication Date Title
EP1963124B1 (fr) Vehicule dote d'un moteur d'entrainement destine a entrainer un train de roulement et un système hydraulique de travail
EP2181221B1 (fr) Mécanisme rotatif d'une excavatrice avec un entraînement hydraulique.
DE3217527C2 (de) Steuereinrichtung für einen hydraulischen doppeltwirkenden Arbeitszylinder
EP1963686B1 (fr) Mécanisme d entraînement hydrostatique
EP2042745B1 (fr) Système d'entraînement hydraulique avec récupération d'énergie
EP2267317B1 (fr) Système hydraulique
WO2007076942A1 (fr) Mécanisme d’entraînement avec fonction de récupération d’énergie et de retard
EP2081787A2 (fr) Entraînement hydrostatique avec récupération de l'énergie de freinage
DE3539220C2 (fr)
DE10331534B4 (de) Hydraulisches Lenksystem für mobile Arbeitsmaschinen
DE102005060992A1 (de) Hydrostatischer Antrieb mit Rückgewinnug von Bremsenergie
DE2557149A1 (de) Vorrichtung zum erzeugen eines oeldrucks fuer ein artilleriegeschuetz o.dgl.
DE2349351B2 (de) Hydrauliksystem fuer eine presse
DE2457210C3 (de) Hydrostatischer Zusatzantrieb für die lenkbaren Antriebsräder eines Fahrzeuges, insbesondere eines Schleppers
DE2737184A1 (de) Hydrostatischer fahrantrieb mit zu- und abschaltung von zusaetzlichen antriebsraedern
EP2024666A1 (fr) Mecanisme d'entrainement hydrostatique comprenant un circuit hydraulique ouvert et un circuit hydraulique ferme
DE102016224401A1 (de) Arbeitshydrauliksystem und Fahrzeug mit dem Arbeitshydrauliksystem
DE102013222744B3 (de) Kompakte hydraulische antriebseinheit und verfahren zu dessen betreiben
DE10331533B4 (de) Steuer- und Stellsystem für ein Hub- und Kippwerk eines Arbeitswerkzeugs in einer mobilen Arbeitsmaschine
DE102020208594B4 (de) Hydrostatischer Zusatzantrieb
DE102021214704A1 (de) Hydraulisches System
DE4337991A1 (de) Hydropneumatisches Antriebssystem
DE4140860A1 (de) Regelbares hydrostatisches getriebe
DE10304665A1 (de) Antrieb mit Hydromaschine
DE1224622B (de) Hydrostatischer Antrieb fuer Fahrzeuge

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

17P Request for examination filed

Effective date: 20080228

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC MT NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK RS

RIN1 Information on inventor provided before grant (corrected)

Inventor name: TIKKANEN, SEPPO

17Q First examination report despatched

Effective date: 20100319

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RIC1 Information provided on ipc code assigned before grant

Ipc: F16H 61/4148 20100101ALI20101214BHEP

Ipc: F16H 61/4078 20100101AFI20101214BHEP

DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20110607