EP2069640B1 - Hydrostatische antriebseinheit - Google Patents

Hydrostatische antriebseinheit Download PDF

Info

Publication number
EP2069640B1
EP2069640B1 EP07785899A EP07785899A EP2069640B1 EP 2069640 B1 EP2069640 B1 EP 2069640B1 EP 07785899 A EP07785899 A EP 07785899A EP 07785899 A EP07785899 A EP 07785899A EP 2069640 B1 EP2069640 B1 EP 2069640B1
Authority
EP
European Patent Office
Prior art keywords
pressure
hydrostatic
drive unit
hydrostatic drive
hydraulic
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.)
Not-in-force
Application number
EP07785899A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2069640A1 (de
Inventor
Jörg Dantlgraber
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2069640A1 publication Critical patent/EP2069640A1/de
Application granted granted Critical
Publication of EP2069640B1 publication Critical patent/EP2069640B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/001—With multiple inputs, e.g. for dual control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
    • F04B1/22—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F15B2211/20584—Combinations of pumps with high and low capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/214—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being hydrotransformers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members

Definitions

  • the invention relates to a hydrostatic drive unit according to the preamble of claim 1.
  • Such hydrostatic drive units are used for example for actuating hydraulic cylinders and have a secondary controlled subsystem, which consists essentially of a hydraulic transformer which is connected to a system with impressed pressure.
  • a hydraulic transformer is mechanically coupled hydrostatic units, one of which is connected to the system with the impressed operating pressure, and the other is connected to the consumer, for example a hydraulic cylinder.
  • the unit connected to the cylinder operates as a pump which is driven by the motor fed by the system with impressed operating pressure.
  • the functions of the hydrotransformer reverse and the unit, previously operating as a motor, now in turn travels the secondary system.
  • the basic structure of such hydrotransformers is described, for example, in the book “ The Hydraulic Trainer “, Volume 6," Hydrostatic Drives with Secondary Control ", Chapter 6; Vogel Buchverlag Würzburg described.
  • a hydrostatic drive unit in which a differential cylinder is actuated by means of a hydraulic transformer.
  • the hydrotransformer is designed with a tank connection, a pressure connection and a working connection, with pressure applied to the pressure connection, for example via a hydraulic accumulator. This pressure also acts in the annulus of the differential cylinder.
  • the bottom-side cylinder chamber is connected to the working connection of the hydrotransformer.
  • the hydrostatic drive system with an additional hydrotransformer whose working connection is connected to the annular space and at the pressure connection of which the pressure applied via a hydraulic accumulator is applied.
  • the cylinder may be made of the same size as in systems with a conventional valve control, it is disadvantageous, however, that due to the second hydraulic transformer, a considerable device complexity is required.
  • hydrostatic drive units with a differential cylinder and two hydrostatic units or a hydrostatic double unit are known, which are connected with their connections to the two pressure chambers of the differential cylinder and with a tank or a feed circuit. The way the units are powered remains open.
  • hydrostatic drive units with a differential cylinder and two hydrostatic units or a hydrostatic double unit known, which are connected with their connections to the two pressure chambers of the differential cylinder and with a hydraulic accumulator. How the units are powered remains open here.
  • the invention has for its object to provide a hydrostatic drive unit which allows a control of a consumer, in particular a hydraulic cylinder with low device complexity.
  • a hydrotransformer used in such a hydrostatic drive unit is in principle made of three hydrostatic units, with two hydrostatic constant units being drivable by an adjustable hydraulic machine.
  • the two ports of a hydrostatic unit with the two pressure chambers of the consumer, for example, the differential cylinder are connected, while a working port of the second hydrostatic unit with the larger of the pressure chambers and a tank port of this hydrostatic unit is connected to a tank.
  • These two hydrostatic units are driven by the adjustable hydromachine, whose pressure connection is connected to a pressure line carrying the impressed pressure and whose tank connection is connected to a tank line leading to the tank.
  • the hydrostatic drive unit is particularly compact, since the variable hydraulic machine together with the constant units is a double axial piston machine, wherein a double unit of the double axial piston machine forms both the constant units and the other unit of the double axial piston machine forms the adjustable hydraulic machine
  • the hydraulic consumer is preferably a differential cylinder, wherein the first pressure chamber has a larger effective area than the second pressure chamber.
  • a second delivery port of the second hydrostatic unit is also connected to the first pressure chamber.
  • the displacement volumes of the two constant units behave according to an advantageous development of each other as the ratio of the piston rod surface to the piston bottom surface.
  • the impressing of the system pressure by means of a hydraulic accumulator, which is chargeable by a storage loading pump.
  • the dynamic behavior of the hydrostatic drive unit can be improved by a bias of the hydraulic cylinder.
  • FIG. 1 shows a circuit diagram of a hydrostatic drive unit 1 for a differential cylinder 2, which has a bottom-side cylinder chamber 4 and a piston rod side annular space 6.
  • the hydrostatic drive unit 1 essentially has a dash-dotted line indicated hydrotransformer 8, consisting of a hydraulic adjusting motor 10, the two constant units, in the present case two constant displacement pumps 12, 14 drives.
  • a pressure port P of the adjusting motor 10 is connected to a pressure line 16, which is impressed on a hydraulic accumulator 18, a system pressure.
  • the hydraulic accumulator 18 is charged by means of a storage loading pump 20.
  • a tank connection of the adjusting motor 10 is connected to a tank T via a tank line 22.
  • a delivery port P of the fixed displacement pump 12 opens into a working line 24 leading to the cylinder chamber 4 of the differential cylinder 2.
  • the suction port T of this constant displacement pump 12 is connected to the tank line 22.
  • a delivery port P of the further constant pump 14 opens into the working line 24, while the other delivery port T - called here for simplicity suction port - is connected via a second working line 26 to the annular space 6.
  • Both constant pumps 12, 14 and the adjusting motor 10 are designed with reversible conveying direction, so that corresponding to the in FIG. 1 As a delivery port designated connections P of the constant pumps can also act as suction ports.
  • the direction of rotation of the adjustment motor 10 is effected by appropriate adjustment of the pivot angle.
  • the displaced from the annular space 6 pressure fluid is summed over the second constant pump 14 to the funded by the constant pump 12 pressure medium flow in the working line 24, so that the differential cylinder 2 extends.
  • FIG. 2 shows a concrete embodiment of such a hydraulic transformer 8, in which the three hydrostatic units are summarized as an axial piston machine in a compact housing.
  • the basic structure of such a "floating-cup axial piston machine” is for example from the post-published application 10 2005 056 631.1 known, so that only the components required for understanding the invention will be described here.
  • Such a hydraulic transformer 8 in Axial piston construction has a housing with a central part 28 which is closed at the end by two connection covers 30, 32.
  • a shaft 34 is mounted, which has approximately centrally a radially projecting drive flange 36, in the axis parallel Kir.Wellenachse 38 a plurality of double piston 40 are inserted, the remote from the drive flange 36, spherical end sections each dip into a cylinder sleeve 42 and limit each with a working space 60 with this.
  • cylindrical sleeves 42 are biased by a spring displaceable against a cylinder drum 44, which in turn is supported on the front side of a swash plate 46 which is pivotally mounted with its convex rear side in a corresponding bearing recess 47.
  • kidneys 48, 50 are formed, which are hydraulically connected to a pressure channel 54 and a tank channel 52, which lead to the pressure port P and the tank port T of the adjustment motor 10.
  • the cylinder drum 44 is rotatably connected via a driver 64 with a bearing portion of the shaft 34. This driver 64 is designed so that the cylinder drum 44 can perform a wobbling motion.
  • control pockets 56, 58 are formed on the convexly executed rear side of the swashplate 46.
  • the limited by a respective cylinder sleeve 42 and an end portion of the double piston 40 working spaces 60 of the axial piston unit are connected by one connecting channel 62 - depending on the angle of rotation of the cylinder drum 44 with one of the control kidneys 48 and 50, so that pressure medium via the pressure channel 52 in Working spaces 60 flow or can be displaced from these via the tank channel 54 to the tank port T.
  • the trained in the swash plate 70 control kidneys 74 and 76 are connected via working channels 80 and 82 with the first working line 24, which in turn opens into the cylinder chamber 4 of the differential cylinder 2.
  • the radially inner control kidney 72 is over another.
  • Working channel 86 with the other working line 26 and the control kidneys 78 connected via a tank channel 84 to the tank line 22, so that the in FIG. 1 Formed pressure fluid flow paths form.
  • each second of the left end portions of the double piston 40 and the respective associated cylinder sleeve 42 limited work spaces 88 via a slanted channel 90 in the cylinder drum 66 with the control kidneys 76 or via a further inclined channel 92 with the control kidney 78 connectable.
  • the intervening work spaces 68 can be connected via the dashed lines indicated channels 94, 96 with the control kidneys 74 and 72, respectively. That is, each second end portion of the double piston 40 to the left of the drive flange 36 is thus a piston of the fixed displacement pump 12, while the intermediate end portions piston of the further constant pump 14 are.
  • Such a design principle is known as a so-called "split flow double pump".
  • the dynamic behavior of the hydrostatic drive unit can be improved by biasing the differential cylinder 2.
  • FIG. 3 is shown a possibility for such a bias. Accordingly, branch from the two working lines 24, 26 bias lines 98 and 100 from.
  • the biasing line 100 leads to a storage line 102, in which a first orifice 104 with a comparatively large diameter is formed.
  • the biasing line 102 is connected on the one hand with a hydraulic accumulator 106 and on the other hand via a second orifice 108 with a comparatively small diameter to the tank T.
  • a branch line 110 branches off from the preload line, in which a third diaphragm 112 and a fourth diaphragm 114 are arranged and which opens into the tank T beyond the fourth diaphragm 114.
  • the biasing line 98 is connected to the region between the two apertures 112, 114. In other words, via the two bias lines 98, 100, a biasing pressure for the differential cylinder 2 is tapped between each associated aperture 104, 108 and 112, 114, wherein the low pressure medium losses through the small apertures 108, 114 to the tank T out in Purchase can be taken.
  • the swash plate 46 In the basic position of the adjusting motor 10 is pivoted back to 0, ie the swash plate 46 according to FIG. 2 is set transversely to the shaft axis 38 with its face facing the cylinder drum 44.
  • the control disk 46 FIG. 2
  • the conveying direction of the constant displacement pumps 12, 14 is reversed by opposing pivoting of the control disk 46, so that corresponding pressure medium from the cylinder chamber 4 via the working line 24 and the constant displacement pump 12 is conveyed into the tank line 22 and from there into the tank T.
  • the constant-displacement pump 14 pressure medium directly from the pressure line 24 via the second working line 26 in the increasing annular space. 6
  • the tilt angle of the adjustment motor is no longer associated with a precisely defined drive speed, but with impressed system pressure a specific torque.
  • Constant pumps 12, 14 were used in the embodiments described above. In principle, however, variable displacement pumps could also be used.
  • a hydrostatic drive unit for supplying pressure medium to a hydraulic consumer with two pressure chambers.
  • the hydrostatic drive unit according to the invention has an adjusting motor and two hydrostatic units which can be driven via the adjusting motor. Via one of the hydrostatic units, pressure medium is conveyed directly from one of the pressure chambers into the other pressure chamber.
  • the further hydrostatic unit conveys pressure fluid from a tank in the latter pressure chamber or depending on the drive direction of this in the tank.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Reciprocating Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
EP07785899A 2006-09-26 2007-07-05 Hydrostatische antriebseinheit Not-in-force EP2069640B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006045442A DE102006045442A1 (de) 2006-09-26 2006-09-26 Hydrostatische Antriebseinheit
PCT/EP2007/005929 WO2008037306A1 (de) 2006-09-26 2007-07-05 Hydrostatische antriebseinheit

Publications (2)

Publication Number Publication Date
EP2069640A1 EP2069640A1 (de) 2009-06-17
EP2069640B1 true EP2069640B1 (de) 2011-12-14

Family

ID=38521083

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07785899A Not-in-force EP2069640B1 (de) 2006-09-26 2007-07-05 Hydrostatische antriebseinheit

Country Status (5)

Country Link
EP (1) EP2069640B1 (zh)
CN (1) CN101517243B (zh)
AT (1) ATE537366T1 (zh)
DE (1) DE102006045442A1 (zh)
WO (1) WO2008037306A1 (zh)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010007137A1 (de) * 2010-02-05 2011-08-11 Hoerbiger Automatisierungstechnik Holding GmbH, 86956 Fluidbetätigter Stellantrieb an einer Armatur
DE102010052559A1 (de) 2010-11-25 2012-05-31 Robert Bosch Gmbh Axialkolbeneinheit mit veränderbarem Verdrängungsvolumen
DE102014226236A1 (de) * 2014-09-29 2016-03-31 Robert Bosch Gmbh Hydraulische Schaltung und Maschine mit einer hydraulischen Schaltung

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19842534A1 (de) * 1998-08-01 2000-02-03 Mannesmann Rexroth Ag Hydrostatisches Antriebssystem für eine Spritzgießmaschine und Verfahren zum Betreiben eines solchen Antriebssystems
JP2001317447A (ja) * 2000-05-09 2001-11-16 Tokimec Inc 液圧装置
JP4454122B2 (ja) * 2000-08-11 2010-04-21 住友建機株式会社 油圧閉回路
DE10214225C1 (de) * 2002-03-22 2003-08-14 Komatsu Mining Germany Gmbh Verfahren zur Steuerung einer hydraulischen Betätigungseinheit
EP1573200B1 (de) * 2002-12-18 2007-02-21 Bosch Rexroth AG Axialkolbenmaschine
DE10343016B4 (de) * 2003-09-17 2010-08-26 Brueninghaus Hydromatik Gmbh Hydraulisches Steuer- und Stellsystem mit Volumenausgleich
DE102004061559A1 (de) * 2004-12-21 2006-06-29 Brueninghaus Hydromatik Gmbh Hydraulischer Antrieb

Also Published As

Publication number Publication date
WO2008037306A1 (de) 2008-04-03
CN101517243B (zh) 2012-02-08
DE102006045442A1 (de) 2008-03-27
EP2069640A1 (de) 2009-06-17
CN101517243A (zh) 2009-08-26
ATE537366T1 (de) 2011-12-15

Similar Documents

Publication Publication Date Title
DE19706114C9 (de) Vorrichtung zur Pulsationsverminderung an einer hydrostatischen Verdrängereinheit
EP1628019B1 (de) Schwenkmotor mit einem Druckbegrenzungsventil
DE102012006289A1 (de) Hydrostatische Axialkolbenmaschine
DE112010004561B4 (de) Hydraulikmotor-Antriebsvorrichtung
DE102008012404A1 (de) Hydrostatische Verdrängereinheit
EP2069640B1 (de) Hydrostatische antriebseinheit
DE19849334B4 (de) Hydrostatische Motoreinheit
WO2006122808A1 (de) Hydrostatische kolbenmaschine nach dem floating-cup-konzept
DE102009021833A1 (de) Hydraulischer Antrieb und Drehschieberventil für einen hydraulischen Antrieb
WO2015090702A2 (de) Axialkolbenmaschine
DE102015223037A1 (de) Vibrationsantrieb mit hydraulischer Pulserzeugungsvorrichtung
DE69732476T2 (de) Rotierende hydraulische umformer
EP1722994B1 (de) Antriebssystem mit gemeinsamen arbeitsdruckanschluss
EP2069641B1 (de) Hydrostatisches getriebe
DE102012006290A1 (de) Hydrotransformator
DE102011105440A1 (de) Hydrostatischer Fahrantrieb
DE1505375C3 (de) Steuervorrichtung für den wahlweise zuschaltbaren hydrostatischen Zusatzantrieb von mindestens einem vom Hauptantrieb eines Fahrzeuges nicht angetriebenen Fahrzeugrad
EP1671032A1 (de) Hydrostatische kolbenmaschine mit zwei hydraulischen kreisläufen
DE102013007668A1 (de) Hydraulisches Antriebssystem für einen Zylinder
DE102022206651A1 (de) Antriebssystem
DE102012218971A1 (de) Hydrostatische Axialkolbenmaschine
DE1955886C3 (de) Hydrostatisches Axialkolbengetriebe
DE102012013572A1 (de) Hydrostatische Taumelscheibenmaschine
DE3520340A1 (de) Axialkolbenverstellmotor
DE3333982A1 (de) Aggregat aus zwei pumpen in schraegscheibenbauform

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: 20090427

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

17Q First examination report despatched

Effective date: 20090914

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

DAX Request for extension of the european patent (deleted)
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 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

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

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502007008861

Country of ref document: DE

Effective date: 20120209

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20111214

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

Ref country code: LT

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: 20111214

LTIE Lt: invalidation of european patent or patent extension

Effective date: 20111214

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

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: 20120315

Ref country code: SI

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: 20111214

Ref country code: LV

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: 20111214

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: 20111214

Ref country code: SE

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: 20111214

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: 20111214

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

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

Ref country code: IS

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: 20120414

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: 20111214

Ref country code: CZ

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: 20111214

Ref country code: SK

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: 20111214

Ref country code: EE

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: 20111214

Ref country code: BG

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: 20120314

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

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: 20120416

Ref country code: PL

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: 20111214

Ref country code: RO

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: 20111214

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

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

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: 20111214

26N No opposition filed

Effective date: 20120917

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502007008861

Country of ref document: DE

Effective date: 20120917

BERE Be: lapsed

Owner name: ROBERT BOSCH G.M.B.H.

Effective date: 20120731

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

Ref country code: MC

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

Effective date: 20120731

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20120705

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 NON-PAYMENT OF DUE FEES

Effective date: 20120705

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: 20120325

Ref country code: LI

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

Effective date: 20120731

Ref country code: CH

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

Effective date: 20120731

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: 20120731

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: 20111214

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

Ref country code: MT

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: 20111214

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 537366

Country of ref document: AT

Kind code of ref document: T

Effective date: 20120731

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: 20120731

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

Ref country code: TR

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: 20111214

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: 20120705

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

Ref country code: HU

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: 20070705

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 10

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 11

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 12

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

Ref country code: IT

Payment date: 20180720

Year of fee payment: 12

Ref country code: FR

Payment date: 20180723

Year of fee payment: 12

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

Ref country code: DE

Payment date: 20180928

Year of fee payment: 12

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502007008861

Country of ref document: DE

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: 20200201

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 NON-PAYMENT OF DUE FEES

Effective date: 20190731

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 NON-PAYMENT OF DUE FEES

Effective date: 20190705