EP3378827A1 - Procédé de fonctionnement d'une installation hydraulique d'un chariot de manutention - Google Patents

Procédé de fonctionnement d'une installation hydraulique d'un chariot de manutention Download PDF

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Publication number
EP3378827A1
EP3378827A1 EP18159628.9A EP18159628A EP3378827A1 EP 3378827 A1 EP3378827 A1 EP 3378827A1 EP 18159628 A EP18159628 A EP 18159628A EP 3378827 A1 EP3378827 A1 EP 3378827A1
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EP
European Patent Office
Prior art keywords
hydraulic pump
temperature
pressure medium
volume flow
consumer
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
EP18159628.9A
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German (de)
English (en)
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EP3378827B1 (fr
Inventor
Sebastian Schauer
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STILL GmbH
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STILL GmbH
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Publication date
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
    • B66F9/075—Constructional features or details
    • B66F9/20—Means for actuating or controlling masts, platforms, or forks
    • B66F9/22—Hydraulic devices or systems
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/045—Compensating for variations in viscosity or temperature
    • 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
    • F15B2211/20538—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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6343—Electronic controllers using input signals representing a temperature
    • 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
    • F15B2211/6346—Electronic controllers using input signals representing a state of input means, e.g. joystick position
    • 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
    • F15B2211/6654—Flow rate control
    • 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
    • F15B2211/75—Control of speed of the output member

Definitions

  • the invention relates to a method for operating a hydraulic system of a truck which has a driven by a drive motor hydraulic pump and at least one driven by the volume flow of the hydraulic pump consumers, wherein in the control of the consumer, the volume flow of the hydraulic pump in response to the control signal of an actuator, in particular a joystick or a hand control lever is controlled.
  • the hydraulic system usually has a constant-displacement pump with a constant delivery volume.
  • a lifting drive for lifting and lowering a lifting device
  • a tilt drive for tilting a mast on which the lifting device is arranged raised and lowered
  • additional consumers such as a side gate for the load handling attachments.
  • an actuator such as a joystick or a hand control lever
  • actuated by the driver of the truck and set according to the deflection of the actuator a certain target speed with a hydraulic motor driving the drive motor is operated.
  • the target speed and the delivery volume of the hydraulic pump results in a certain of the hydraulic pump funded flow (flow), with which the consumer is supplied.
  • the designed as a fixed displacement pump hydraulic pump is thus operated in the control of a consumer with a controlled speed, which is solely dependent on the deflection of the actuator.
  • a setpoint speed is generated, with which the hydraulic pump designed as a fixed displacement pump is operated, i. for different deflections of the actuator different target speeds are generated.
  • the disadvantage here is that in the generation and thus the specification of these target speeds but not the load pressure of the consumer and the viscosity-dependent and speed-dependent volumetric efficiency of the hydraulic pump is taken into account. It follows that for the same deflection of the actuator, ie a certain deflection point of the actuator, the consumer different-sized volume flows and thus a varying volume flow is provided at different viscosities of the pressure medium. This effect is based on the fact that, in the case of a hydraulic pump designed as a fixed displacement pump, the volume flow varies with fluctuating viscosity of the pressure medium at the same load pressure.
  • the present invention has for its object to provide a method for operating a hydraulic system of a truck of the type mentioned, which avoids the disadvantages mentioned.
  • This object is achieved in that in the control of the consumer, the volume flow of the hydraulic pump in response to the temperature of the pressure medium is controlled such that in the control of the flow rate of the hydraulic pump compensation of the influences of the temperature of the pressure medium on the funded by the hydraulic pump Volume flow takes place, whereby over the entire temperature operating range of the pressure medium for the Actuator signal is provided a constant volume flow to the consumer.
  • a constant volume flow of the hydraulic pump is thus provided at a certain deflection of the actuator and thus a certain control signal of the actuator regardless of the temperature of the pressure medium and thus over the entire temperature operating range of the pressure medium, with which the consumer is operated.
  • the hydraulic pump is designed as a fixed displacement pump with a constant displacement and is controlled in the control of the consumer, the flow rate of the hydraulic pump in response to the control signal of the actuator, in particular a joystick or a manual control lever, by a speed specification of the drive motor.
  • the actuator in particular a joystick or a manual control lever
  • a speed specification of the drive motor in a trained as constant pump hydraulic pump can be controlled by specifying a speed of the constant pump in a simple way promoted by the constant pump volume flow.
  • a temperature-dependent adaptation of the speed specification of the drive motor is carried out according to an embodiment of the invention for compensating the effects of the temperature of the pressure medium on the volume flow delivered by the hydraulic pump.
  • the volume flow delivered by a hydraulic pump designed as a fixed displacement pump can be controlled in a simple manner so that a compensation of the influences of the temperature of the pressure medium on the volume flow delivered by the hydraulic pump takes place in order to maintain a constant over the entire temperature operating range of the pressure medium for the control signal of the actuator Provide flow for the consumer.
  • the temperature-dependent adaptation of the speed specification is carried out such that with increasing temperature of the pressure medium, the speed specification of the drive motor is increased. Since the volume flow of the hydraulic pump - at constant speed and load pressure of the consumer - decreases with increasing temperature of the pressure medium, can be achieved with increasing the temperature of the pressure medium in a secure manner with increasing the speed specification of the drive motor, that the hydraulic pump at a certain deflection of the actuator regardless of the temperature of the pressure medium delivers a constant volume flow.
  • the temperature-dependent adaptation of the speed specification is effected by a factorization with a viscosity-dependent factor. This makes it possible in a simple way, with increasing temperature of the pressure medium to increase the speed specification of the drive motor.
  • the characteristic diagram of the volumetric efficiency of the hydraulic pump is determined for this purpose, and a plurality of characteristic curves for constant volume flows are determined, and the viscosity-dependent factor is determined from the plurality of characteristic curves for constant volume flows.
  • the map of the volumetric efficiency of the hydraulic pump is for this purpose preferably determined for target operating points including the occurring load pressures of the consumer and the desired constant volume flows with which the consumer is to be operated. If, furthermore, several characteristic curves for constant volumetric flows are determined, which are each a function of the volumetric efficiency of the hydraulic pump, the viscosity-dependent factor used for the temperature-dependent adaptation of the rotational speed specification can be determined from these characteristics.
  • the temperature of the pressure medium is preferably measured with a temperature sensor, which detects in particular the temperature of the pressure medium in a container of the hydraulic system.
  • FIG. 1 is a circuit diagram of a hydraulic system 1 of the invention of an industrial truck shown.
  • the hydraulic system 1 has a driven by a drive motor 2 hydraulic pump 3 and at least one consumer 4, which is driven by the volume flow Q of the hydraulic pump 3.
  • the hydraulic pump 3 is operated in an open circuit and sucks with a suction line 5 pressure fluid from a container 6 and promotes the flow rate Q in a delivery line 7, which is in communication with the consumer 4.
  • the load pressure p of the consumer 4 is set in the delivery line 7.
  • the hydraulic pump 3 is formed in the illustrated embodiment as a fixed displacement pump with a constant displacement.
  • the drive motor 2 driving the hydraulic pump 3 is designed, for example, as an electric motor.
  • An electronic control device 10 is connected on the input side to an actuator 11, for example a joystick or a manual control lever, and is On the output side with the drive motor 2 in conjunction to specify a speed n for driving the hydraulic pump 3.
  • an actuator 11 for example a joystick or a manual control lever
  • the drive motor 2 is On the output side with the drive motor 2 in conjunction to specify a speed n for driving the hydraulic pump 3.
  • driving the load 4 is determined by the electronic control device 11 based on the actuating signal generated by the actuated actuator 11 a speed n soll for the drive motor 2, in response to the control signal of the actuator 11 a corresponding volume flow Q of the hydraulic pump 3 for actuating the Consumer 4 to produce.
  • the drive motor 2 thus provides the rotational speed n and a corresponding torque M for driving the hydraulic pump 3
  • the volumetric efficiency ⁇ vol of the hydraulic pump 3 is the variable variable.
  • the volumetric efficiency ⁇ vol of the hydraulic pump 3 is dependent on the rotational speed n, the viscosity of the pressure medium, which changes over the temperature T of the pressure medium and the type of the pressure medium and thus is a function of the temperature T of the pressure medium and the type of the pressure medium.
  • FIG. 2 is a diagram of the volumetric efficiency ⁇ vol of the hydraulic pump 3 of FIG. 1 represented by the viscosity of the pressure medium.
  • the viscosity of the pressure medium is shown on the ordinate of the volumetric efficiency ⁇ vol of the hydraulic pump 3 and on the abscissa.
  • the viscosity of the pressure medium is shown on the ordinate of the volumetric efficiency ⁇ vol of the hydraulic pump 3 and on the abscissa.
  • the viscosity of the pressure medium is shown.
  • the region X an optimum viscosity range for the operation of the hydraulic pump 3, which is not equal, but is smaller than the entire temperature operating range of the pressure medium of the hydraulic system 1.
  • FIG. 3 is a graph of the viscosity of the pressure medium of the hydraulic system 1 of FIG. 1 about the temperature T shown.
  • the viscosity of a pressure medium is shown on the ordinate and the temperature T on the abscissa.
  • the FIG. 3 is the dependence of the viscosity of a pressure medium on the temperature T to recognize.
  • the viscosity of the pressure medium decreases with increasing temperature T.
  • the viscosity of the pressure medium is thus a function of the temperature T.
  • FIG. 4 According to the diagram of FIG. 4 in which the volume flow Q of the hydraulic pump 3 is the FIG. 1 is shown on the temperature T of the pressure medium, wherein on the ordinate the volume flow Q of the hydraulic pump 3 and on the abscissa the temperature T of the pressure medium is shown, it can be seen that the hydraulic pump 3, at constant speed n and constant load pressure p, a flow Q promotes the changes due to the dependence of the volumetric efficiency ⁇ vol of the hydraulic pump 3 of the viscosity on the temperature T of the pressure medium. With increasing temperature T of the pressure medium, the volume flow Q decreases. The hydraulic pump 3 thus promotes according to the diagram of FIG.
  • a temperature sensor 12 detecting the temperature T of the pressure medium in the container 6 is provided, which is connected on the input side to the electronic control device 10.
  • the volume flow Q of the hydraulic pump 3 in response to the control signal of the actuator 11 by a speed specification (target speed) n soll the drive motor 2 is controlled in the control of the consumer 4, to compensate for the effects of the temperature T of the pressure medium on the from the hydraulic pump 3 funded volume flow Q a temperature-dependent adjustment of the speed specification (target speed) n should the drive motor 2 performed.
  • the rotational speed n soll of the drive motor 3 and thus the speed n soll of the hydraulic pump 2 is adjusted in such a manner depending on the temperature T of the pressure medium measured with the temperature sensor 12 such that regardless of the temperature T of the pressure medium for a certain deflection and thus a determined control signal of the actuator 11, a constant volume flow Q is generated to supply the load 4. It is thus the consumer 4 at a certain deflection of the actuator 11 by an individual speed n of the hydraulic pump 3 in response to the respective temperature of the pressure medium independent of the temperature of the pressure medium volume flow Q and thus a constant temperature over the temperature Q provided ,
  • n To the temperature-dependent adjustment of the speed setting (target speed) n is to perform the drive motor 2 and to compensate for the effects of varying temperature T of the pressure medium to the volume flow Q in order to achieve a constant over the temperature T flow rate Q for a particular deflection of the actuator 11, the exact data to the hydraulic pump 3 with respect to the volume flow Q, which is a function of the rotational speed n, the load pressure p and the volumetric efficiency ⁇ vol , and the temperature T of the pressure medium are required.
  • the temperature T of the pressure medium is measured by means of the temperature sensor 12 and provided to the electronic control device 10.
  • the map of the volumetric efficiency ⁇ vol of the hydraulic pump 3 is to be determined.
  • the map is here in particular for Target operating points including the occurring load pressures p and desired respectively constant volume flows Q1, Q2, Q3 to Qn, with which the consumer 4 is to be operated to determine.
  • Speed n viscosity a ⁇ t of the pressure medium .
  • the viscosities of the pressure medium for various temperatures can be determined, for example -10 ° C, -5 ° C, 0 ° C, + 5 ° C, + 15 ° C, + 35 ° C, + 65 ° C, + 85 ° C and + 95 ° C.
  • a constant volume flow Q is thus provided with a corresponding deflection of the actuator 11 by means of the individual speed of the hydraulic pump 3 in response to the temperature T of the pressure medium to the consumer 4 independent of temperature.
  • a viscosity-dependent factor k can be determined for each consumer 4 and stored in the electronic control device 10, so that each consumer 4 is parameterized separately.
  • a generally valid viscosity-dependent factor k can be stored in the electronic control device 10, which can be used with justifiable excess supply of the consumer 4 with the volume flow Q for all consumers 4.
  • the load pressure p of the consumer 4 can be detected with a pressure sensor and made available to the electronic control device 10, whereby the effects of the load pressure p on the volumetric efficiency ⁇ vol of the hydraulic pump 3 can be compensated.
  • the inventive method has a number of advantages.
  • the driver of the truck for the same deflection of the actuator 11, ie a certain deflection point of the actuator 11, such as a joystick or a hand control lever, receives the same operating speed of the consumer 4 over the entire temperature operating range of the pressure medium. This leads to increased comfort, since consumer movements are carried out optimally. In addition, reproducible operating speeds of the driven consumer 4 over the entire Operating range achieved. With the method according to the invention, the driver of the truck is no longer forced to readjust the deflection on the actuator in order to achieve an expected operating speed of the driven consumer 4.
  • the hydraulic pump 3 is always operated in the optimum speed range and thus always leads at the operating point to the lowest noise pollution.
  • optimum viscosity range X can be achieved by a reduced rated speed of the hydraulic pump 3 and / or by a reduced speed dynamics extended life (running time) of the hydraulic pump 3. Cavitation in the hydraulic pump 3 at low starting temperatures and thus a high viscosity of the pressure medium and a lubricant film break in the hydraulic pump 3 at high operating temperatures and thus a low viscosity of the pressure medium can be prevented. This can be done in the method according to the invention by implementing a warm-up phase and / or cooling phase.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Structural Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Civil Engineering (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
EP18159628.9A 2017-03-24 2018-03-02 Procédé de fonctionnement d'une installation hydraulique d'un chariot de manutention Active EP3378827B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102017106390.0A DE102017106390A1 (de) 2017-03-24 2017-03-24 Verfahren zum Betrieb einer Hydraulikanlage eines Flurförderzeugs

Publications (2)

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EP3378827A1 true EP3378827A1 (fr) 2018-09-26
EP3378827B1 EP3378827B1 (fr) 2019-12-25

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EP (1) EP3378827B1 (fr)
DE (1) DE102017106390A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110307217A (zh) * 2018-11-28 2019-10-08 林德（中国）叉车有限公司 一种叉车液压系统的热车控制方法和系统
WO2020104174A1 (fr) * 2018-11-20 2020-05-28 Liebherr-Aerospace Lindenberg Gmbh Procédé de surveillance d'une pompe à moteur électrique régulée en vitesse de rotation d'un circuit hydraulique dans un aéronef et système hydraulique pour la mise en œuvre du procédé
WO2021022682A1 (fr) * 2019-08-06 2021-02-11 南通锻压设备如皋有限公司 Procédé de commande combinée de vitesse et de pression de presse hydraulique orbitale
CN113338384A (zh) * 2021-05-27 2021-09-03 三一重机有限公司 电驱动正流量液压控制系统、方法和作业机械

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018222364A1 (de) * 2018-12-19 2020-06-25 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Steuerungsvorrichtung und Verfahren zur Regelung eines Volumenstroms eines Fluids in einem Antriebsstrang eines Kraftfahrzeugs
DE102018133098A1 (de) 2018-12-20 2020-06-25 Still Gmbh Verfahren zum Betreiben einer Hydraulikanlage eines Flurförderzeugs

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US6005360A (en) * 1995-11-02 1999-12-21 Sme Elettronica Spa Power unit for the supply of hydraulic actuators
DE10128583A1 (de) * 2001-06-13 2002-12-19 Linde Ag Hydraulikanlage für ein batterie-elektrisch betriebenes Flurförderzeug
JP2010255780A (ja) * 2009-04-27 2010-11-11 Toyooki Kogyo Kk 液圧装置

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JP2005299450A (ja) 2004-04-08 2005-10-27 Toyota Industries Corp ポンプ制御装置
US7798781B2 (en) 2006-02-22 2010-09-21 Hamilton Sundstrand Corporation Metering pump with self-calibration and health prediction
DE102006033026A1 (de) 2006-06-27 2008-01-03 Robert Bosch Gmbh Verfahren zur Regelung einer Pumpe zum Fördern eines flüssigen Mediums
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DE112009001698B4 (de) 2008-08-12 2020-02-20 Magna Powertrain Bad Homburg GmbH Anordnung und Verfahren zur unterbrechungsfreien Versorgung eines Hydrauliksystems mit einem Fluid
JP2012250817A (ja) 2011-06-03 2012-12-20 Nippon Yusoki Co Ltd 油圧システムおよび該油圧システムを備えたフォークリフト
DE102014216736A1 (de) 2014-08-22 2016-02-25 Jungheinrich Aktiengesellschaft Verfahren zum Steuern einer kombinierten Dreh-Schub-Bewegung

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6005360A (en) * 1995-11-02 1999-12-21 Sme Elettronica Spa Power unit for the supply of hydraulic actuators
DE10128583A1 (de) * 2001-06-13 2002-12-19 Linde Ag Hydraulikanlage für ein batterie-elektrisch betriebenes Flurförderzeug
JP2010255780A (ja) * 2009-04-27 2010-11-11 Toyooki Kogyo Kk 液圧装置

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020104174A1 (fr) * 2018-11-20 2020-05-28 Liebherr-Aerospace Lindenberg Gmbh Procédé de surveillance d'une pompe à moteur électrique régulée en vitesse de rotation d'un circuit hydraulique dans un aéronef et système hydraulique pour la mise en œuvre du procédé
CN110307217A (zh) * 2018-11-28 2019-10-08 林德（中国）叉车有限公司 一种叉车液压系统的热车控制方法和系统
WO2021022682A1 (fr) * 2019-08-06 2021-02-11 南通锻压设备如皋有限公司 Procédé de commande combinée de vitesse et de pression de presse hydraulique orbitale
CN113338384A (zh) * 2021-05-27 2021-09-03 三一重机有限公司 电驱动正流量液压控制系统、方法和作业机械
CN113338384B (zh) * 2021-05-27 2023-03-10 三一重机有限公司 电驱动正流量液压控制系统、方法和作业机械

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Publication number Publication date
DE102017106390A1 (de) 2018-09-27
EP3378827B1 (fr) 2019-12-25

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