EP1577257B1 - Appareil de levage hydraulique pour chariot élévateur électrique - Google Patents

Appareil de levage hydraulique pour chariot élévateur électrique Download PDF

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Publication number
EP1577257B1
EP1577257B1 EP05004255A EP05004255A EP1577257B1 EP 1577257 B1 EP1577257 B1 EP 1577257B1 EP 05004255 A EP05004255 A EP 05004255A EP 05004255 A EP05004255 A EP 05004255A EP 1577257 B1 EP1577257 B1 EP 1577257B1
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EP
European Patent Office
Prior art keywords
load
hydraulic
lifting cylinder
lifting
lowering
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
EP05004255A
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German (de)
English (en)
Other versions
EP1577257A3 (fr
EP1577257A2 (fr
Inventor
Nis-Georg Nissen
Thomas Stolten
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.)
Jungheinrich AG
Original Assignee
Jungheinrich AG
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Filing date
Publication date
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Publication of EP1577257A2 publication Critical patent/EP1577257A2/fr
Publication of EP1577257A3 publication Critical patent/EP1577257A3/fr
Application granted granted Critical
Publication of EP1577257B1 publication Critical patent/EP1577257B1/fr
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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
    • 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
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
    • 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
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line

Definitions

  • the invention relates to a hydraulic lifting device for battery-powered industrial trucks according to the preamble of patent claim 1.
  • a hydraulic lifting device in which at least one hydraulic lifting cylinder is acted upon in load lifting operation by a pump which is driven by an electric machine.
  • the pump works as a hydraulic motor and drives the electric machine as a generator (use sinks).
  • the Senkzweig a hydraulic flow restrictor is arranged, on which drops in certain operating points, the entire hydraulic pressure and which assumes the load holding.
  • the Senkzweig is connected between a check valve and the input of the hydraulic pump.
  • At least one secondary consumer is provided, which can be supplied with the medium of the lifting cylinder in the lowering operation of the lifting cylinder.
  • the electric machine is always operated in the same direction, and the other hydraulic consumer can be supplied directly with hydraulic energy from the lowering process, so that efficiency losses are minimized.
  • a speed control ensures a load-independent control of the lowering speed both in generator operation of the electric machine as well as in a controller alone via a valve assembly. Both the lifting and the lowering speed via a speed control of the electric machine. This can happen that the lowering speed is undesirably high, if due to the high volume flow demand of the additional consumer, the speed of the electric machine is increased accordingly.
  • a similar lifting device as that described is out DE 100 10 670 C2 known.
  • Senkzweig a throttle valve and a pressure compensator are arranged, and A connection point between the throttle valve and the pressure compensator is connected to the input of the hydraulic pump, while the output of the pressure compensator is led to the tank.
  • An electro-hydraulic lifting device has become known in which the volume flows to the lifting cylinder or to the tank on the one hand and to secondary consumers on the other hand are divided in the pressure line by means of a proportional three-way flow control device.
  • the disadvantage here is that the lift valve in the tank line behind the flow control device, which can also act as a priority valve, is arranged. As a result, flow losses occur in load-lowering operation.
  • the invention has for its object to provide a hydraulic lifting device for battery-powered trucks, with the minimum flow losses are achieved regardless of the respective volume flow requirements.
  • the lift valve in the lifting branch is arranged downstream of the branch of the line to the secondary consumer.
  • the line is connected upstream of the control valve via a pressure compensator to the tank.
  • the pressure fluid displaced from the lifting cylinder and discharged via the lowering branch, the pump, the pressure branch and the tank line into the tank flows exclusively through the pressure compensator. This allows a high efficiency in energy recovery over the known solutions.
  • the pressure compensator with the pressure in the pressure line (in lifting mode) or the pressure on the secondary consumer is driven in order to derive the excess unsolicited amount (load sensing).
  • an inlet pressure compensator is arranged upstream of the secondary consumer. Because of this configuration as a load-sensing system in conjunction with 2-way flow controller (input pressure compensator) for controlling the secondary consumer, it is possible to supply several auxiliary functions simultaneously with pressure medium from the load-lowering operation and their operating speed independently depending on the operation of the respective Setpoint adjuster to regulate.
  • the speed control device causes the rotational speed of the electric machine not to be raised by the theoretically resulting differential rotational speed.
  • the auxiliary consumers will only be provided with as much volume flow as is available from the load-lowering mode. As a result, an unwanted acceleration of the lowering process is avoided.
  • the sole figure shows a circuit diagram for a device according to the invention.
  • a hydraulic pump 5 can be seen, which is coupled to an electric machine 6.
  • the electrical machine is controlled by a speed control device, not shown, in its speed, wherein the speed setpoint is specified via a speed setpoint generator, which is actuated by an operator in an industrial truck.
  • a reach truck which has a lifting cylinder 1, a tilting cylinder 2, a side thrust cylinder 3 and a push cylinder 4.
  • the pump 5 provides the pressure medium for all consumers (main consumer lifting cylinder 1 and secondary consumers 2 to 4) available, wherein the pressure medium is sucked from a tank 19 via a check valve 17 in the tank line 7.
  • the individual valves with which the different consumers are controlled are housed in block 18.
  • a lifting valve 7 and a check valve 20 are arranged in a pressure or lifting line 9 to the lifting cylinder 1.
  • the lifting speed is determined by the speed of the electric motor 6 and this in turn via the setpoint generator, not shown.
  • a Senkzweig 8 is connected between the lifting cylinder 1 and the check valve 20, in which a throttle valve 11 is arranged.
  • the other end is connected to the tank line 7 between a check valve 17 and the pump 5. From the lifting cylinder backflowing medium is therefore always passed through the pump 5.
  • a branch line 10 is connected to the pressure line 9. It serves to supply the mentioned auxiliary consumers.
  • two pressure compensators 15 are connected to the line 10, whose output is connected to a line 14, which leads to a control valve 16, respectively.
  • the control valves 16 With the help of the control valves 16, the speed of the auxiliary consumers is controlled. Tilting cylinder and side thrust cylinder are operated together via the control valve 16, via a further valve 22 whose position determines to which of the cylinders 2, 3, the hydraulic medium flows.
  • a tank line 12 is connected, in which a pressure compensator 13 is arranged.
  • the hydraulic medium reaches the tank 19, wherein in the conduit 12 a filter 24 is arranged and parallel to this a check valve 26th
  • a first shuttle valve 28 is connected end to the input of the control valves 16.
  • the position of the valve ball depends on which pressure at the two inputs is the larger one.
  • In the middle of the shuttle valve is connected to the input of a second shuttle valve 30 whose other end is in communication with the pressure line 9. Again, the position of the valve ball depends on which pressure at the two inputs of the shuttle valve is the larger.
  • the middle of the second shuttle valve 30 is connected to a control input of the pressure compensator 13. In this way, a load-sensing system is created.
  • the hydraulic unit operates as a pump, and the lifting speed depends on the default by the operator via a setpoint generator. As a result, the opening width of the lift valve is specified. Occur during the lifting volume flow requirements of the auxiliary consumers, they are also supplied via the branch line 10 with hydraulic medium, the amount is set by the control valves 16, and the pressure compensators 15 ensure that this happens independent of load.
  • hydraulic medium passes through the throttle valve 11 to the pump 5 and drives it, so that the electric machine 6 can operate as a generator and can feed electricity back into the battery.
  • the hydraulic medium passes through the branch 10 and the pressure compensator 13 to the tank 19, which happens almost lossless.
  • the globe valve 7 is naturally closed.
  • volume flow requirements occur during the lowering process also with regard to the secondary consumers, these can also be supplied. Unused hydraulic medium is in turn returned via pressure compensator 13. If the pressure and volume flow from the load-lowering operation exceeds the pressure and volume flow requirement of one or more secondary consumers, in addition to the supply of one or more auxiliary consumers, parallel generation of excess power from the load-lowering operation via pump and electric machine 6 is possible.
  • Mautileer can be supplied independently in pressure load mode with pressure medium to be controlled in dependence on the operation of the control valves 16 and the associated setpoint generator. Is the volume flow Requirement of one or more auxiliary consumers greater than the available from the Lastsenkvorgang volumetric flow rate, the speed control causes that the speed of the electric motor 6 is not raised by the theoretically resulting differential speed.
  • the secondary consumers are only provided with the volume flow available from the load-lowering operation. As a result, an unwanted acceleration of the lowering process is avoided.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structural Engineering (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Civil Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Forklifts And Lifting Vehicles (AREA)

Claims (3)

  1. Appareil de levage hydraulique pour chariots élévateurs électriques, comprenant au moins un cylindre de levage hydraulique (1), une pompe hydraulique (5) fonctionnant en tant que pompe (5) en régime de levage de charge, alimentant le cylindre de levage en fluide de pression, et fonctionnant en tant que moteur en régime d'abaissement de charge, entraînée par le fluide de pression déplacé par le cylindre de levage (1), une machine électrique (6) couplée à la pompe hydraulique (5), fonctionnant en régime de levage de charge en tant que moteur électrique et en régime d'abaissement de charge en tant que générateur, un dispositif de réglage de la vitesse pour la machine électrique (6), la vitesse de la machine électrique (6) pouvant être réglée par le dispositif de réglage de la vitesse en fonction de l'actionnement d'un transmetteur de valeur de consigne, un arrangement de vannes à soupape (7) dans une branche de levage (9) conduisant au cylindre de levage (1), une branche d'abaissement (8) entre le cylindre de levage (1) et une liaison entre une soupape anti-retour (17) et une entrée de la pompe hydraulique (5), un limiteur de débit volumétrique (11) dans la branche d'abaissement (8), un arrangement de soupapes de dérivation qui connecte une sortie de la pompe hydraulique (5) avec le réservoir (18) et au moins un autre consommateur hydraulique (2, 3, 4) qui peut être alimenté par la pompe hydraulique (5) par le biais d'une soupape de commande (16) coordonnée, la vanne à soupape (7) dans la branche de levage (9) étant disposée en aval de l'embranchement d'une conduite (10) vers le consommateur secondaire (2, 3, 4), caractérisé en ce que la conduite (10) vers le consommateur secondaire est connectée en amont de la soupape de commande (16) avec le réservoir (19) par le biais d'une balance de pression (13), et la balance de pression (13) est activée avec la pression plus élevée respectivement du cylindre de levage (1) ou du consommateur secondaire (2, 3, 4) en vue de la dérivation du débit volumétrique excédentaire non demandé (load sensing).
  2. Appareil selon la revendication 1, caractérisé en ce qu'une balance de pression d'entrée (15) est disposée en amont de la soupape de commande (16).
  3. Appareil selon la revendication 1 ou 2, caractérisé en ce que le dispositif de réglage de la vitesse pour la machine électrique (6) est conçu de telle façon que la vitesse prédéfinie par le processus d'abaissement de charge n'est pas augmentée lorsque la demande de débit volumétrique du consommateur secondaire (2, 3, 4) est supérieure à l'offre de débit volumétrique du processus d'abaissement de charge.
EP05004255A 2004-03-11 2005-02-26 Appareil de levage hydraulique pour chariot élévateur électrique Active EP1577257B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004011913 2004-03-11
DE102004011913A DE102004011913B4 (de) 2004-03-11 2004-03-11 Hydraulische Hubvorrichtung für batteriebetriebene Flurförderzeuge

Publications (3)

Publication Number Publication Date
EP1577257A2 EP1577257A2 (fr) 2005-09-21
EP1577257A3 EP1577257A3 (fr) 2005-09-28
EP1577257B1 true EP1577257B1 (fr) 2009-01-14

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP05004255A Active EP1577257B1 (fr) 2004-03-11 2005-02-26 Appareil de levage hydraulique pour chariot élévateur électrique

Country Status (3)

Country Link
US (1) US7181910B2 (fr)
EP (1) EP1577257B1 (fr)
DE (2) DE102004011913B4 (fr)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007010697A1 (de) * 2007-03-06 2008-09-11 Jungheinrich Aktiengesellschaft Flurförderzeug
DE102007028864A1 (de) * 2007-03-27 2008-10-02 Robert Bosch Gmbh Hydraulische Steueranordnung
US7980073B2 (en) * 2008-05-08 2011-07-19 Caterpillar Inc. Hybrid system for a powertrain and hydraulic system
DE102012102092B4 (de) 2012-03-13 2024-04-25 Still Gesellschaft Mit Beschränkter Haftung Hydraulikanlage einer mobilen Arbeitsmaschine, insbesondere eines Flurförderzeugs
DE102012024647A1 (de) * 2012-12-17 2014-06-18 Jungheinrich Aktiengesellschaft Hydraulische Hubvorrichtung für ein batteriebetriebenes Flurförderzeug
SE1350633A1 (sv) * 2013-05-24 2014-11-25 BAE Systems Hägglunds Aktiebolag Förfarande och system för styrning av hydraulanordning
US9975426B2 (en) 2013-06-26 2018-05-22 Parker-Hannifin Manufacturing Limited Energy efficient electric vehicle control system
DE102014108370B4 (de) * 2014-06-13 2020-10-01 Jungheinrich Aktiengesellschaft Hydraulische Hubvorrichtung für ein batteriebetriebenes Flurförderzeug
DE102014114526A1 (de) 2014-10-07 2016-04-07 Linde Material Handling Gmbh Hydraulisches Antriebssystem einer batterie-betriebenen mobilen Arbeitsmaschine
DE102016124506A1 (de) * 2016-12-15 2018-06-21 Jungheinrich Aktiengesellschaft Flurförderzeug mit einer Steuereinheit zur Regelung der Bewegung einer Last sowie ein entsprechendes Verfahren
DE102017131164A1 (de) 2017-12-22 2019-06-27 Linde Material Handling Gmbh Hydraulisches Antriebssystem einer mobilen Arbeitsmaschine, insbesondere eines Flurförderzeugs
CN111148905B (zh) * 2018-09-05 2021-08-27 株式会社日立建机Tierra 电动式液压工程机械的液压驱动装置

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4127342C2 (de) * 1991-08-19 1995-02-16 Danfoss As Hydraulisches System mit einer Pumpe
DE4402653C2 (de) * 1994-01-29 1997-01-30 Jungheinrich Ag Hydraulische Hubvorrichtung für batteriebetriebene Flurförderzeuge
DE4423644C2 (de) * 1994-07-06 1998-10-01 Buchholz Hydraulik Hydraulische Steuervorrichtung
DE29911686U1 (de) * 1999-07-06 1999-09-16 Heilmeier & Weinlein Elektrohydraulischer Hubmodul
DE10010670C2 (de) * 2000-03-04 2003-11-06 Jungheinrich Ag Hydraulische Hubvorrichtung für batteriebetriebene Flurförderzeuge
DE10224730B4 (de) * 2001-06-29 2012-09-27 Linde Material Handling Gmbh Hydraulische Steuereinrichtung

Also Published As

Publication number Publication date
US7181910B2 (en) 2007-02-27
DE102004011913A1 (de) 2005-10-13
DE102004011913B4 (de) 2005-12-29
DE502005006449D1 (de) 2009-03-05
EP1577257A3 (fr) 2005-09-28
EP1577257A2 (fr) 2005-09-21
US20050198950A1 (en) 2005-09-15

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