EP2655895A1 - Mécanisme d'entraînement hydraulique - Google Patents

Mécanisme d'entraînement hydraulique

Info

Publication number
EP2655895A1
EP2655895A1 EP11784424.1A EP11784424A EP2655895A1 EP 2655895 A1 EP2655895 A1 EP 2655895A1 EP 11784424 A EP11784424 A EP 11784424A EP 2655895 A1 EP2655895 A1 EP 2655895A1
Authority
EP
European Patent Office
Prior art keywords
pump
hydraulic
pressure
torque
variable
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.)
Granted
Application number
EP11784424.1A
Other languages
German (de)
English (en)
Other versions
EP2655895B1 (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

Links

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 patent claim 1.
  • EP 0 805 922 B1 discloses a hydraulic pump control system of an aircraft using a variable displacement hydraulic pump driven by a variable speed electric motor.
  • the speed of the motor is hereby controlled so that its reduction rate at a system request reduction is smaller than its increase rate at a system request magnification. This means that, for example, with decreasing demand pressure, the first
  • Stroke volume of the pump is reduced, whereas at increasing demand pressure initially increases the engine speed.
  • EP 464 286 B1 Another prior art is EP 464 286 B1, from which an electro-hydraulic drive unit is also known.
  • This drive unit uses a variable speed operable electric motor for driving a variable displacement pump.
  • the variable displacement pump is adjusted by means of a spring to a position with maximum displacement, from which it is adjusted in the direction of minimum displacement when the pressure in the hydraulic system rises above a certain pressure value.
  • DE 10 2007 007 005 A1 discloses an electro-hydraulic control arrangement with a displacement-variable pump which is driven by a variable-speed electric motor.
  • a two-position regulator is provided, which switches the pump to a maximum or minimum delivery position, depending on an overflow or underflow condition with respect to a pressure threshold.
  • the invention accordingly relates to a hydraulic drive for one or more consumers or to a hydraulic system with a displacement-variable pump, which is mechanically coupled to a variable-speed drive motor, and a controller for adjusting the stroke volume of the pump.
  • the pump is torque-controlled. This means that to drive the pump a certain torque should not be exceeded.
  • the torque which results from the product of system pressure and stroke volume, which is referred to as the amount of pressure fluid delivered by the pump per revolution, is below the specified torque even at maximum displacement, the torque control does not intervene.
  • Acceleration and load at the stop by a pressure valve can be specified so high that the product of pressure and stroke volume reaches the predetermined value, the pump is adjusted in the direction of smaller displacement.
  • the product of pressure and stroke volume remains at least approximately constant.
  • a drive motor with a relatively small maximum torque can be used, making the drive more cost effective and also its operation by reduced power consumption of the engine is more economical.
  • torque detection device is here to be used to designate any device which is capable of drawing conclusions about the current torque load of the drive motor, for example a torque sensor which is placed on the drive motor or its output shaft Current measuring device, which measures the actual current consumption of the motor and determines its output torque.It is also possible to detect the current pressure in the hydraulic system connected downstream of the pump and to control or regulate the stroke volume so that the specified maximum torque is not exceeded.
  • Torque detection / or determination device for a variable displacement known per se, in which a valve piston of a control valve in the one adjustment of a spring force, which sets the maximum torque, and in the other adjustment direction is acted upon by a force that resulting from the stroke volume dependent point of attack of a pump pressure applied to the piston on a lever.
  • the drive motor is variable in speed.
  • the stroke volume of the pump is reduced to limit the required torque on the engine, this would result in a hydraulically induced movement of one or more consumers (eg, a lift cylinder) slowing down.
  • the speed of the drive motor can be increased with reduced displacement of the pump, whereby the volume flow generated by the swung back pump speed increases again without the output torque increases.
  • the hydraulic load is at a stop when the pressure rises, only one pressure is to be maintained, so that the speed of the drive motor does not increase, on the contrary, it is more likely to decrease.
  • the power consumption of the engine can be kept below a substantially (quasi) constant value, so that the engine with respect to its maximum possible
  • Power output can be designed smaller.
  • Fig. 1 shows in juxtaposition
  • Fig. 2 shows a hydraulic control / control for a
  • variable displacement pump according to the invention.
  • Hydraulic drive shown using two independently driven constant displacement pumps. Each pump is therefore driven by its own, possibly variable-speed motor. This structure is comparatively complicated and expensive. In addition, there is a large amount of space, making this solution rather uneconomical.
  • An improvement provides the well-known hydraulic drive according to the middle representation in the figure. This drive also uses two fixed displacement pumps, but they are driven together by a single motor.
  • One of the constant-displacement pumps can be connected via a valve, a 2/2-way valve with an open position and a blocking position can optionally be switched directly to a tank, whereby this pump is taken from the downstream hydraulic system. In this way, the engine can be relieved.
  • the pump 2 may be designed as a swash plate pump whose swash plate inclination is continuously or stepwise variable.
  • 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 this case a piston-cylinder unit can be actuated.
  • the only displacement-variable pump 2 is operated by a single, preferably variable-speed drive motor 10, for example an electric motor, which is mechanically coupled to the pump 2 via a drive shaft.
  • a single, preferably variable-speed drive motor 10 for example an electric motor, which is mechanically coupled to the pump 2 via a drive shaft.
  • a control unit 11 is provided for the drive motor 10, to which at least one torque sensor and a system pressure sensor and a speed sensor and a sensor for detecting the currently set stroke volume (swash plate tilt) of the pump 2 are connected (all sensors are not shown).
  • the control unit 11 is programmed or programmable so that the hydraulic drive 1 builds up a predeterminable (input) consumer or system pressure and holds it.
  • T Actual output torque of the motor.
  • the drive motor 10 to make variable speed. Therefore, the rotational speed of the engine 10 can be increased as the discharge capacity of the pump 2 is reduced to maintain the output torque constant to maintain the demanded actual consumer pressure.
  • FIG. 2 shows a representation 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 Ausschwenkkolben 75 which limits a control chamber 101, a return spring 85 on the Ausschwenkkolben 75 and a Einschwenkkolben 76 which limits a control chamber 102 ,
  • a high-pressure passage 103 and a low-pressure or suction passage 104 run in the housing 12.
  • the actuation chamber 101 is permanently connected to a high-pressure passage 103 via a passage 105.
  • a control valve 80 is constructed on the housing 12.
  • This consists of a torque control valve 06 and a pressure control valve part 107, which in a rest position via a first Input and its control output a control output of the torque control valve 106 switches through to a control line 108 which leads to the control chamber 102 on Einschwenkkolben 76.
  • a second input of the pressure regulating valve 107 is connected to the high pressure passage 103.
  • an input of the torque control valve 106 is connected to the high pressure passage 103, while a second input of this torque control valve 106 is open to tank pressure having interior of the housing 12.
  • a control piston of the pressure control valve 107 is acted upon in the sense of a reduction of the swivel angle of the swash plate 43 from the pressure in the high pressure line 103 and in the opposite direction by an adjustable spring.
  • a two-armed lever 1 15 is mounted, on whose one lever arm guided in the housing of a return element and via the channel 105, the adjusting chamber 101 and the bore 92 in Ausschwenkkolben 75 with the pressure in the high-pressure passage 103 acted piston 116th attacks.
  • the distance of the point of attack changes with the swivel angle of the swashplate 43.
  • the other arm of the lever 115 is located between the one end of a control piston of the torque control valve 106 and an adjustable spring 117 engaging at least approximately opposite the lever arm.
  • the control piston of the torque control valve 106 acted upon by an adjustable spring 118 in the direction of the lever arm.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Computer Hardware Design (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Reciprocating Pumps (AREA)

Abstract

L'invention concerne un mécanisme d'entraînement hydraulique pour un consommateur hydraulique ou pour un système hydraulique, comprenant une pompe à cylindrée variable qui est couplée mécaniquement à un moteur d'entraînement, de préférence un moteur à régime variable. Le mécanisme d'entraînement hydraulique comprend aussi une commande pour régler au moins la cylindrée de la pompe et éventuellement le régime du moteur d'entraînement. Selon l'invention, on utilise un dispositif de détection et/ou de détermination de couple qui détecte ou calcule un couple de sortie courant du moteur d'entraînement, et en réponse à celui-ci, la cylindrée de la pompe est réglée à une valeur à laquelle le couple de sortie courant se situe à la valeur maximale réglée ou en dessous de celle-ci.
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 true EP2655895A1 (fr) 2013-10-30
EP2655895B1 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)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021228677A1 (fr) * 2020-05-11 2021-11-18 Moog Gmbh Procédé de détermination d'un état d'usure actuel d'une machine hydrostatique

Families Citing this family (4)

* 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
DE102021200100A1 (de) 2021-01-08 2022-07-14 Robert Bosch Gesellschaft mit beschränkter Haftung Hydraulische Getriebeeinheit, insbesondere für Tiefseeanwendungen

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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
US3935707A (en) * 1974-07-22 1976-02-03 General Signal Corporation Hydraulic control system
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
GB9119448D0 (en) * 1991-09-12 1991-10-23 Vickers Systems Ltd System controls
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
CA2213457C (fr) 1995-03-14 2005-05-24 The Boeing Company Systeme de commande de pompe hydraulique pour avion
DE19538649C2 (de) * 1995-10-17 2000-05-25 Brueninghaus Hydromatik Gmbh Leistungsregelung mit Load-Sensing
US6748739B1 (en) * 1999-07-14 2004-06-15 Yuken Kogyo Kabushiki Kaisha Hydraulic power system
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
JP4424370B2 (ja) * 2007-05-02 2010-03-03 ダイキン工業株式会社 油圧ユニット及びそれを備えた建設機械

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021228677A1 (fr) * 2020-05-11 2021-11-18 Moog Gmbh Procédé de détermination d'un état d'usure actuel d'une machine hydrostatique

Also Published As

Publication number Publication date
EP2655895B1 (fr) 2020-01-22
TWI608172B (zh) 2017-12-11
US20130336812A1 (en) 2013-12-19
DE102011108285A1 (de) 2012-06-28
TW201239206A (en) 2012-10-01
WO2012084093A1 (fr) 2012-06-28
CN103261706A (zh) 2013-08-21

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