EP2655895B1 - Entraînement hydraulique - Google Patents

Entraînement hydraulique Download PDF

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Publication number
EP2655895B1
EP2655895B1 EP11784424.1A EP11784424A EP2655895B1 EP 2655895 B1 EP2655895 B1 EP 2655895B1 EP 11784424 A EP11784424 A EP 11784424A EP 2655895 B1 EP2655895 B1 EP 2655895B1
Authority
EP
European Patent Office
Prior art keywords
pump
torque
hydraulic
pressure
stroke volume
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.)
Active
Application number
EP11784424.1A
Other languages
German (de)
English (en)
Other versions
EP2655895A1 (fr
Inventor
Patric BUECKER
Stefan NIEDERNHOEFER
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 EP2655895A1 publication Critical patent/EP2655895A1/fr
Application granted granted Critical
Publication of EP2655895B1 publication Critical patent/EP2655895B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/06—Control using electricity
    • F04B49/065—Control using electricity and making use of computers
    • 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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F15B11/0423—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling pump output or bypass, other than to maintain constant speed
    • 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
    • F04B2203/00—Motor parameters
    • F04B2203/02—Motor parameters of rotating electric motors
    • F04B2203/0207—Torque
    • 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
    • F04B2205/00—Fluid parameters
    • F04B2205/06—Pressure in a (hydraulic) circuit
    • 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
    • F15B2211/20515—Electric motor
    • 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
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • 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
    • F15B2211/26—Power control functions
    • 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
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6309—Electronic controllers using input signals representing a pressure the pressure being a pressure source supply pressure
    • 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
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/633—Electronic controllers using input signals representing a state of the prime mover, e.g. 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6333—Electronic controllers using input signals representing a state of the pressure source, e.g. swash plate angle
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle
    • 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
    • F15B2211/6655—Power control, e.g. combined pressure and flow rate control

Definitions

  • the present invention relates to a hydraulic drive for a hydraulic consumer according to the preamble of claim 1.
  • Torque-controlled pumps are generally known.
  • One example is the DE 39 19 175 A1 directed.
  • a hydraulic drive according to the preamble of claim 1 is known.
  • This provides for the arrangement of a variable-speed electric motor, which in this case drives two constant pumps. At least one of the pumps can be switched on / off depending on the current consumer pressure, in that this pump is preferably switched to circulation, preferably with the larger stroke volume. In this way, the motor drive can be designed with a comparatively small torque.
  • the EP 0 805 922 B1 discloses an aircraft hydraulic pump control system using a variable displacement hydraulic pump driven by a variable speed electric motor.
  • the speed of the motor is regulated in such a way that its rate of reduction in the case of a reduction in the system requirements is less than the rate of increase in the case of an increase in the system requirements. This means that, for example, when the demand pressure decreases, the stroke volume of the pump is first reduced, whereas when the demand pressure increases, the engine speed increases first.
  • EP 464 286 B1 Another state of the art is EP 464 286 B1 called, from which an electro-hydraulic control is also known.
  • This control uses a variable-speed motor to operate a pressure-controlled variable pump.
  • the variable displacement pump is at a position with maximum by means of a spring Stroke volume set, from which it is adjusted in the direction of the minimum stroke volume when the pressure in the hydraulic system rises above a certain pressure value.
  • the DE 10 2007 007 005 A1 finally discloses an electro-hydraulic control arrangement with a variable-displacement pump, which is driven by a variable-speed electric motor.
  • a two-point controller is provided, which switches the pump to a maximum or minimum delivery position, depending on whether the pressure threshold value has exceeded or fallen below.
  • a hydraulic drive for a hydraulic system at least consisting of a displacement variable (variable stroke volume) pressure medium source (hydraulic pump) and a variable-speed electric motor
  • the drive compared to the prior art Technology has improved properties.
  • One goal is to make the hydraulic drive less expensive.
  • Another goal is to reduce the control effort.
  • the invention accordingly relates to a hydraulic drive for one / more consumers or for a hydraulic system with a variable-displacement pump, which is mechanically coupled to a variable-speed electric motor, and a controller for adjusting the stroke volume of the pump.
  • the pump is torque-controlled. This means that a certain torque should not be exceeded to drive the pump. As long as the torque, which results from the product of system pressure and stroke volume, which is called the pressure medium quantity pumped by the pump, even at maximum Stroke volume is below the specified torque, the torque control does not intervene.
  • the pump is adjusted in the direction of a smaller stroke volume.
  • the product of pressure and displacement remains at least approximately constant.
  • torque detection / or determination device is to be used here to provide any device that is suitable for drawing conclusions about the current torque load on the electric motor.
  • This device can be, for example, a torque sensor that is placed on the electric motor or its output shaft or a current measuring device that measures the current current consumption of the motor and uses this to determine its output torque. It is also possible to record the current pressure in the hydraulic system downstream of the pump and to adjust the stroke volume in a controlled or regulated manner so that the specified maximum torque is not exceeded.
  • a torque detection / or determination device is a torque regulator known per se for a variable displacement pump, in which a valve piston of a control valve is acted upon in one adjustment direction by a spring force which specifies the maximum torque and in the other adjustment direction by a force which arises from the point of application of a piston on a lever, which is acted upon by the pump pressure, depending on the stroke volume.
  • the electric motor is variable in speed. Accordingly, if the stroke volume of the pump is reduced in order to limit the required torque on the electric motor, this would result in a hydraulically induced movement of one or more consumers (for example a lifting cylinder) being slowed down. Do you want the movement maintained, the speed of the electric motor can be increased with a reduced stroke volume of the pump, as a result of which the volume flow generated by the swiveled-back pump rises again as a function of the speed, without the output torque increasing.
  • the power consumption of the electric motor can be kept below an essentially (quasi) constant value, so that the electric motor can be designed to be smaller with regard to its maximum possible power output.
  • FIG.1 According to the attached Fig.1 is shown in the left representation an already known hydraulic drive that uses two independently driven constant pumps. Each pump is therefore powered by its own, possibly variable-speed motor driven. This structure is comparatively complex and expensive. There is also a large space requirement, which makes this solution rather uneconomical.
  • the hydraulic drive which is also known, according to the illustration in the middle of the figure.
  • This drive also uses two constant pumps, but they are driven together by a single motor.
  • One of the constant pumps can be switched directly to a tank via a valve, if there is a 2/2-way switching valve with an open and a locked position, whereby this pump is removed from the downstream hydraulic system. In this way, the motor can be relieved suddenly.
  • the pump 2 can be designed as a swash plate pump whose swash plate inclination can be changed continuously or step by step.
  • This pump 2 is connected on the output side to a hydraulic system 4, for example consisting of an actuating valve 6, via which a consumer 8, in the present case a piston-cylinder unit, can be actuated.
  • variable-displacement pump 2 is operated by a single variable-speed electric motor 10, which is mechanically coupled to the pump 2 via a drive shaft.
  • the delivery capacity of the pump 2 is reduced in this way, the hydraulically activated movement of a consumer would slow down. This is avoided if, when the delivery capacity of the pump 2 is reduced to keep the output torque constant, the speed of the electric motor is increased in order to maintain the consumer movement speed.
  • FIG. 2 shows an illustration of the pressure medium pump according to the present invention.
  • a housing 12 the hydraulic drive with a cylinder drum 40, a drive shaft 22, a swash plate 43, a swivel-out piston 75, which delimits a control chamber 101, a return spring 85 on the swivel-out piston 75 and a swivel-in piston 76, which delimits a control chamber 102 ,
  • a high-pressure duct 103 and a low-pressure or suction duct 104 run in the housing 12.
  • the actuating chamber 101 is permanently connected to a high-pressure duct 103 via a duct 105.
  • a control valve 80 is built on the housing 12. This consists of a torque control valve 106 and a pressure control valve 107, which in a rest position via a first Input and its control output through a control output of the torque control valve part 106 to a control line 108 which leads to the actuating chamber 102 on the pivoting piston 76.
  • a second inlet of the pressure regulating valve 107 is connected to the high pressure duct 103.
  • one input of the torque control valve 106 is connected to the high-pressure duct 103, while a second input of this torque control valve 106 is open to the interior of the housing 12 having tank pressure.
  • a regulating piston of the pressure regulating valve 107 is acted upon by the pressure in the high-pressure line 103 in the sense of reducing the swivel angle of the swash plate 43 and, in the opposite direction, by an adjustable spring.
  • a two-armed lever 115 is mounted, on the one lever arm of which a piston 116 which is guided in the housing of a return element and acts on the pressure in the high-pressure duct 103 via the duct 105, the actuating chamber 101 and the bore 92 in the swing-out piston 75 ,
  • the distance of the point of attack changes with the swivel angle of the swash plate 43.
  • the other arm of the lever 115 is located between the one end of a control piston of the torque control valve part 106 and an adjustable spring 117 which acts on the lever arm at least approximately opposite.
  • the control piston of the torque control valve part 106 in the direction of the lever arm by an adjustable spring 118.
  • the spring 117 and the spring 118 which is set weaker than the spring 117, generate a fixed torque in one direction on the lever 115.
  • the high pressure in the channel 103 uses the active surface of the piston 116 to generate a torque on the lever 115 which is opposite to the fixed torque and which depends on the position of the pivoting piston 75 or generally on the swivel angle of the swash plate 43. At a given pressure, the torque generated by the two springs can only be balanced at a certain swivel angle.
  • valve piston of the torque control valve part 106 is moved out of its control position, so that pressure medium flows in to the control chamber 102 or pressure medium can flow out of the control chamber 102 until another swivel angle is reached, at which balance between the torques again occurs Lever 115 prevails.

Claims (4)

  1. Entraînement hydraulique pour un consommateur hydraulique (8) ou un système hydraulique (4) comprenant une pompe à déplacement variable (2) qui est accouplée mécaniquement à un moteur électrique à vitesse de rotation variable (10), et une commande (12) pour le réglage du volume de travail de la pompe (2), caractérisé en ce que la pompe (2) présente une régulation de couple, c'est-à-dire que pour l'entraînement de la pompe, un couple prédéterminé ne doit pas être dépassé, une régulation du couple ne s'établissant pas tant que le couple qui résulte du produit de la pression du consommateur ou du système et du volume de travail de la pompe est situé en dessous du couple prédéterminé, même dans le cas d'un volume de travail maximal, et si la pression du consommateur ou du système est si élevée que le produit de la pression du consommateur ou du système et du volume de travail de la pompe atteint la valeur prédéfinie, la pompe est alors réglée dans le sens d'un volume de travail plus petit par la régulation de couple.
  2. Entraînement hydraulique selon la revendication 1, caractérisé par un dispositif de détection ou de détermination de pression pour détecter la pression actuelle au niveau du consommateur (8) ou dans le système hydraulique (4), la pompe (2) étant ajustée de telle sorte que l'on ait la relation T = const = P x V, T(const) étant la valeur du couple délivré prédéterminée du moteur électrique, P étant la pression du consommateur/du système hydraulique et V étant le volume de travail de la pompe.
  3. Entraînement hydraulique selon la revendication 2, caractérisé en ce que la pompe (2) est munie d'un régulateur de couple mécanique-hydraulique (106).
  4. Entraînement hydraulique selon l'une quelconque des revendications 1 à 3, caractérisé en ce que la vitesse de rotation du moteur électrique (10) est ajustée en fonction du volume de travail actuel de la pompe (2), de telle sorte qu'une vitesse de déplacement prédéterminée du consommateur hydraulique soit obtenue.
EP11784424.1A 2010-12-22 2011-11-11 Entraînement hydraulique Active EP2655895B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102010055864 2010-12-22
DE102011108285A DE102011108285A1 (de) 2010-12-22 2011-07-21 Hydraulischer Antrieb
PCT/EP2011/005668 WO2012084093A1 (fr) 2010-12-22 2011-11-11 Mécanisme d'entraînement hydraulique

Publications (2)

Publication Number Publication Date
EP2655895A1 EP2655895A1 (fr) 2013-10-30
EP2655895B1 true EP2655895B1 (fr) 2020-01-22

Family

ID=44992858

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11784424.1A Active EP2655895B1 (fr) 2010-12-22 2011-11-11 Entraînement hydraulique

Country Status (5)

Country Link
US (1) US20130336812A1 (fr)
EP (1) EP2655895B1 (fr)
DE (1) DE102011108285A1 (fr)
TW (1) TWI608172B (fr)
WO (1) WO2012084093A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2557233B2 (fr) * 2011-08-12 2022-06-01 ABI Anlagentechnik-Baumaschinen-Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH Appareil de travail doté d'un entraînement hydraulique pour travaux de construction profonds
DE102013224657A1 (de) * 2013-12-02 2015-06-03 Robert Bosch Gmbh Hydraulische Anordnung
DE102014009420B4 (de) * 2014-06-25 2023-03-23 Zf Cv Systems Hannover Gmbh Druckluftversorgungsanlage, pneumatisches System und Verfahren zum Steuern einer Druckluftversorgungsanlage
DE102020112660A1 (de) * 2020-05-11 2021-11-11 MOOG Gesellschaft mit beschränkter Haftung Verfahren zum Bestimmen eines momentanen Verschleißzustandes einer hydrostatischen Maschine
DE102021200100A1 (de) * 2021-01-08 2022-07-14 Robert Bosch Gesellschaft mit beschränkter Haftung Hydraulische Getriebeeinheit, insbesondere für Tiefseeanwendungen

Citations (3)

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Publication number Priority date Publication date Assignee Title
US3935707A (en) * 1974-07-22 1976-02-03 General Signal Corporation Hydraulic control system
US5320499A (en) * 1991-09-12 1994-06-14 Vickers Systems Limited Open-loop hydraulic supply system
US20100115800A1 (en) * 2007-05-02 2010-05-13 Toshiyuki Sakai Hydraulic unit and construction machine including the same

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DE1911695C3 (de) * 1969-03-03 1975-01-02 Mannesmann-Meer Ag, 4050 Moenchengladbach Leistungsregler mit Druckabschneidung für Hydraulikpumpen oder -motoren der Axialkolben-Schrägscheiben-Bauart
DE1922145A1 (de) * 1969-04-25 1970-10-29 Bellows Valvair Kaemper Gmbh Kombinationsregler
DE3919175A1 (de) * 1989-06-12 1990-12-13 Hydromatik Gmbh Regeleinrichtung fuer eine verstellbare pumpe
US5052909A (en) 1990-01-19 1991-10-01 Cincinnati Milacron Inc. Energy-conserving injection molding machine
US5141402A (en) * 1991-01-29 1992-08-25 Vickers, Incorporated Power transmission
JP3707742B2 (ja) * 1994-12-09 2005-10-19 株式会社小松製作所 可変容量型油圧ポンプの制御装置
DE69617207T2 (de) 1995-03-14 2002-05-08 Boeing Co Steuersystem für eine flugzeugflüssigkeitspumpe
DE19538649C2 (de) * 1995-10-17 2000-05-25 Brueninghaus Hydromatik Gmbh Leistungsregelung mit Load-Sensing
WO2001006126A1 (fr) * 1999-07-14 2001-01-25 Yuken Kogyo Kabushiki Kaisha Systeme a puissance hydraulique
EP1387090B1 (fr) 2002-08-02 2014-04-30 Bosch Rexroth AG Dispositif à actionnement hydraulique
DE102007007005B4 (de) 2007-02-08 2021-12-02 Robert Bosch Gmbh Elektrohydraulische Steueranordnung

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3935707A (en) * 1974-07-22 1976-02-03 General Signal Corporation Hydraulic control system
US5320499A (en) * 1991-09-12 1994-06-14 Vickers Systems Limited Open-loop hydraulic supply system
US20100115800A1 (en) * 2007-05-02 2010-05-13 Toshiyuki Sakai Hydraulic unit and construction machine including the same

Also Published As

Publication number Publication date
TWI608172B (zh) 2017-12-11
DE102011108285A1 (de) 2012-06-28
CN103261706A (zh) 2013-08-21
WO2012084093A1 (fr) 2012-06-28
US20130336812A1 (en) 2013-12-19
TW201239206A (en) 2012-10-01
EP2655895A1 (fr) 2013-10-30

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