WO1997020146A1 - Verfahren und vorrichtung zur ansteuerung einer hydroanlage eines arbeitsgerätes - Google Patents
Verfahren und vorrichtung zur ansteuerung einer hydroanlage eines arbeitsgerätes Download PDFInfo
- Publication number
- WO1997020146A1 WO1997020146A1 PCT/DE1996/001934 DE9601934W WO9720146A1 WO 1997020146 A1 WO1997020146 A1 WO 1997020146A1 DE 9601934 W DE9601934 W DE 9601934W WO 9720146 A1 WO9720146 A1 WO 9720146A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- hydraulic
- pressure
- hydraulic cylinder
- cylinder
- piston
- Prior art date
Links
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
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
- F15B11/036—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of servomotors having a plurality of working chambers
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
- F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
-
- 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
- F15B2211/3056—Assemblies of multiple valves
- F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-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
- F15B2211/40—Flow control
- F15B2211/405—Flow control characterised by the type of flow control means or valve
- F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
-
- 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
- F15B2211/40—Flow control
- F15B2211/41—Flow control characterised by the positions of the valve element
- F15B2211/413—Flow control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
-
- 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
- F15B2211/40—Flow control
- F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
- F15B2211/41509—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a 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
- F15B2211/40—Flow control
- F15B2211/42—Flow control characterised by the type of actuation
- F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
-
- 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
- F15B2211/40—Flow control
- F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line
-
- 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
- F15B2211/625—Accumulators
-
- 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
- F15B2211/665—Methods of control using electronic components
- F15B2211/6653—Pressure 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
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7051—Linear output members
- F15B2211/7055—Linear output members having more than two chambers
-
- 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
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/88—Control measures for saving energy
Definitions
- the invention relates to a method for controlling a multi-stage hydraulic cylinder of a working tool acting against a load and a hydraulic system of a working tool working according to the method according to the preamble of claim 3.
- hydraulic cylinders are, in addition to the hydraulic motor, an indispensable device for converting hydraulic energy into mechanical energy.
- a hydraulic pump is usually driven by a motor and hydraulic fluid is drawn in from a tank and conveyed through the pressure line of the hydraulic system to the hydraulic cylinder.
- the direction of movement of the piston in the hydraulic cylinder can be controlled via a directional valve in the pressure line between the hydraulic pump and hydraulic cylinder.
- the hydraulic cylinder loaded with a load represents a resistance for the hydraulic fluid, the pressure in the hydraulic cylinder increasing until the resulting force is sufficient to move the piston against the resistance of the load.
- the maximum movable force is essentially determined by the maximum pump pressure and the effective diameter of the hydraulic cylinder.
- the maximum travel speed of the piston of the hydraulic cylinder depends on the maximum flow rate of the hydraulic pump. In the event that rapid actuating movements of the hydraulic cylinder are required, a high pump output must be made available. In order to keep the pump output low, a hydraulic accumulator is provided in the pressure line Pump is filled if the volume flow required to extend the hydraulic cylinder is less than the maximum pump volume flow during a work cycle. If the maximum volume flow is required to quickly extend the hydraulic cylinder in one operating state, the difference to the volume flow of the pump can be taken from the hydraulic accumulator. The use of these hydraulic accumulators thus allows the maximum pump output to be reduced.
- the invention has for its object to provide a method for controlling a hydraulic cylinder and a hydraulic system of an implement that allow operation of the implement with minimized energy requirements with minimal expenditure on device technology.
- the measure of providing a hydraulic cylinder with a large number of active surfaces and controlling these active surfaces of the hydraulic cylinder as a function of a detected working pressure in the pressure line allows the pressure in the pressure line to the hydraulic cylinder to be adjusted so that it corresponds approximately to that of the hydraulic accumulator, so that at least part of the back-flowing hydraulic fluid can be used to load the hydraulic accumulator when the hydraulic cylinder is retracted.
- the energy requirement of the hydraulic system can be reduced compared to conventional solutions, only a minimal outlay in terms of device technology being required, since the directional control valves can be actuated via comparatively inexpensive hydraulic or electrical control devices.
- the hydraulic cylinder has three active surfaces, two of which act in the extension direction and one active surface in the retracting direction of the hydraulic cylinder or, more precisely, the piston of the hydraulic cylinder, each active surface having an electrically or hydraulically actuable 3/2-way valve assigned.
- the three effective surfaces can be combined as required by suitable control of the directional control valves, so that five pressure levels can be set.
- a particularly simple and compact structure of the hydraulic cylinder is obtained if it is designed with a cup-shaped differential piston, the effective surface formed on the piston rear side and the effective surface formed by a blind hole in the differential piston acting in the extension direction, while the ring surface of the differential piston acts in the direction of retraction.
- a pressure sensor is provided in the pressure line, which forms the input signal for the preferably electrical or hydraulic control unit.
- FIG. 1 shows a circuit diagram of a cylinder drive for a hoist.
- the lifting mechanism shown has a lifting cylinder 1, the piston 2 of which is loaded with a load F which can be moved by extending or retracting the piston 2.
- the piston 2 is designed and has a differential design a blind hole inner bore 4, which opens into the rear of the piston, hereinafter called the piston surface 6.
- the piston 2 is guided in a cylinder jacket 8 which, in the exemplary embodiment shown, is formed with a central column 10 which extends coaxially through the interior of the cylinder jacket 8 and which plunges into the inner bore 4 of the piston 2.
- the cylinder space surrounded by the cylinder jacket 8 is formed by the central column 10 as an annular space in which the piston 2 is guided.
- the radially widened collar section 12 of the piston 2 is guided on the inner surfaces of the cylinder jacket 8 and sealed by means of seals 14.
- the part 16 of the piston 2 on the piston rod side has a cup-shaped cross section and, with its lateral surfaces, penetrates an annular passage recess 18, which is formed in the end face of the cylinder jacket 8 on the piston rod side. Sealing devices 14 for sealing the cylinder face face are in turn provided in the passage recess 18.
- the first cylinder chamber 20 is delimited in the radial direction by the cylinder jacket 8 and the center column 10 and in the axial direction by the lower inner end face of the cylinder jacket 8 and by the piston surface 6.
- the second cylinder space 22 is formed by the end section of the inner bore 4 and the end face of the center column 10.
- the third cylinder chamber 24 is on the one hand through the annular surface 26 of the collar portion 12 of the piston 2 and on the other hand through the inner surface of the upper ⁇ representation according to the figure) end face of the cylinder jacket 8 and on the other hand limited by the outer circumference of the piston rod-side, radially stepped section 16 of the piston 2 and by the inner circumferential surface of the cylinder jacket 8.
- the effective surfaces of the cylinder spaces are thus formed by the surface AI of the piston surface 6, the surface A2 of the ring surface 26 and the end surface A3 of the inner bore 4.
- Two connections 28 and 30 are formed on the cylinder jacket 8 and open into the cylinder space 20 and 24, respectively.
- the central column 10 of the cylinder jacket 8 is penetrated by an axial connection bore 32 which opens into the second cylinder chamber 22.
- the connections 28, 30 and the connection bore 32 are connected to working lines 34, 36, 38, via which hydraulic fluid can be supplied to the respective cylinder spaces 20, 24 and 22.
- the working lines 34, 36, 38 are led to three essentially identical 3/2-way valves 40a, b, c, which are biased into a basic position (not shown) via a spring. In this switching position, a working connection A is connected to a pressure connection T of each directional valve 40a, b, c.
- the pressure connections P of the three way valves 40a, b, c are led via connecting lines to a common pressure line 42, which is connected to a connection D of a proportional valve 44.
- a connection D of a proportional valve 44 In the end position of the proportional valve 44 shown, the port D is connected to a pump port P ', while a tank port T is shut off. In the other end position of the proportional valve 44, the connection D is connected to a tank T.
- a pump line 46 is connected to the pump connection P 'of the proportional valve 44 and is connected to a variable displacement pump 48.
- a branch line branches off from the pump line 46 to a hydraulic accumulator 50, which can be designed, for example, as a bladder accumulator.
- the directional control valves 40a, b, c are designed as electrically actuable solenoid valves, so that when the respective electromagnet 41 is excited, the directional control valve 40 is brought from the basic position into the switching position shown, in which the respective connection B is connected to a tank connection T. .
- the control of the electromagnets 41 of the directional control valves 40a, b, c takes place via a control unit 52, by means of which the directional control valves 40a, b, c can be selectively controlled.
- the signal from a pressure sensor 54 which detects the pressure in the pressure line 42 and outputs a signal to the control unit 52, is used as the input signal for the control unit 52.
- AI M x A3 AI 2 x A2
- five effective areas can be selected that are 1 to 5 times the smallest area, i.e. the end face A3 of the inner bore 4.
- the directional control valves 40a, b, c are activated in such a way that a pressure - as will be explained in more detail below - is established in the pressure line 42, which is approximately equal to the system pressure in the hydraulic accumulator 50.
- a setpoint table is stored in the control device, according to which the pressure in the pressure line 42 when the piston 2 is extended is less than the pressure in the hydraulic valve 44 by approximately the control pressure difference and greater than by the control pressure difference in the hydraulic valve 50 when the piston 2 is retracted is the system pressure in the hydraulic accumulator 50.
- This measure ensures that when hydraulic fluid is displaced from the cylinder spaces of the lifting cylinder 1, the latter can be guided back into the hydraulic accumulator 50 and does not have to be released into the tank “unused”. In this way, the energy consumption of the system can be minimized considerably compared to conventional solutions, with only a minimal outlay in terms of device technology being required.
- the mode of operation of the device according to the invention will be briefly explained below.
- the switching position 5 is first preselected, in which the maximum effective area AI + A3 is preset by energizing the electromagnets of the directional control valves 40a and 40b and thus the third cylinder chamber 24 is not supplied with hydraulic fluid. Furthermore, the proportional valve 44 is brought into a position in which the connections D and P 'are connected to one another, so that hydraulic fluid from the pump 48 or from the hydraulic accumulator 50 is introduced into the cylinder spaces 20 and 22, so that the pressure increases in these rooms until the load F is raised. Immediately after the load F has been raised, the pressure in the pressure line 42 is detected by the pressure sensor 54 and passed on to the control unit 52 as an input signal.
- the directional control valves 40a, b, c are then controlled in such a way that a pressure level is established in the pressure line 42 by a suitable choice of the active surfaces (AI to A3), that is about the control pressure difference lower than the system pressure in the pressure accumulator 50 (lifting).
- the setpoint is changed in such a way that the pressure in the pressure line 42 is greater than the pressure in the hydraulic accumulator 50 by the control pressure difference.
- the control device 52 also allows the compensation of short-term fluctuations in the entry and extension movement, whereby according to the preset target value table by switching the directional control valves 40a, b, c to possible pressure fluctuations in the pressure line 42 and thus in the cylinder spaces 20, 22 and 24 can be reacted without hydraulic fluid from the pump 48 to a considerable extent must be promoted.
- a pressure is set which is higher than the pressure in the hydraulic accumulator 50 by the control pressure difference in the valve 44 (Pr j - Pp-)
- the piston 2 is lowered in a defined manner in the valve 44, hydraulic medium flowing from D to P ′ into the accumulator 50.
- the switching position DT of the valve 44 is necessary to relieve the cylinder spaces 20, 22 and 24.
- control device is designed as an electrically acting device; of course, the control device can also be designed to act hydraulically, wherein the directional control valves 40 can also be designed to be hydraulically controllable.
- control device can also be designed to act hydraulically, wherein the directional control valves 40 can also be designed to be hydraulically controllable.
- other configurations of the lifting cylinder 1 or the valves shown are also conceivable without departing from the basic principle according to the invention.
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- Engineering & Computer Science (AREA)
- Structural Engineering (AREA)
- Mechanical Engineering (AREA)
- Transportation (AREA)
- Life Sciences & Earth Sciences (AREA)
- Civil Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Geology (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP96945157A EP0862697B1 (de) | 1995-11-24 | 1996-10-11 | Verfahren und vorrichtung zur ansteuerung einer hydroanlage eines arbeitsgerätes |
DE59605729T DE59605729D1 (de) | 1995-11-24 | 1996-10-11 | Verfahren und vorrichtung zur ansteuerung einer hydroanlage eines arbeitsgerätes |
US09/068,402 US6145307A (en) | 1995-11-24 | 1996-10-11 | Method and device for controlling a hydraulic installation of a utility vehicle |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19543876.0 | 1995-11-24 | ||
DE19543876A DE19543876A1 (de) | 1995-11-24 | 1995-11-24 | Verfahren und Vorrichtung zur Ansteuerung einer Hydroanlage eines Arbeitsgerätes |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1997020146A1 true WO1997020146A1 (de) | 1997-06-05 |
Family
ID=7778339
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE1996/001934 WO1997020146A1 (de) | 1995-11-24 | 1996-10-11 | Verfahren und vorrichtung zur ansteuerung einer hydroanlage eines arbeitsgerätes |
Country Status (4)
Country | Link |
---|---|
US (1) | US6145307A (de) |
EP (1) | EP0862697B1 (de) |
DE (2) | DE19543876A1 (de) |
WO (1) | WO1997020146A1 (de) |
Families Citing this family (25)
Publication number | Priority date | Publication date | Assignee | Title |
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EP1019885B1 (de) * | 1997-09-17 | 2004-05-12 | Advanced Motion Technologies LLC | Bewegungen erteilendes gerät |
US6468082B1 (en) | 1997-09-17 | 2002-10-22 | Advanced Motion Technologies, Llc | Motion-imparting apparatus |
JP2002522710A (ja) * | 1998-08-06 | 2002-07-23 | マネスマン レックスオート アクチェンゲゼルシャフト | ハイドロ変圧器 |
DE19931973A1 (de) † | 1999-07-09 | 2001-01-11 | Wabco Gmbh & Co Ohg | Einrichtung zum Steuern einer Stelleinrichtung für ein Getriebe |
JP3782710B2 (ja) * | 2001-11-02 | 2006-06-07 | 日邦興産株式会社 | 油圧プレス装置 |
DE10336279A1 (de) * | 2003-08-07 | 2005-03-03 | Bosch Rexroth Ag | Einrichtung zur Steuerung des Ziehvorgangs bei einer Transferpresse |
GB0511908D0 (en) * | 2005-06-11 | 2005-07-20 | Stannah Lifts Ltd | Improvements in or relating to drive systems |
AT503408B1 (de) * | 2006-04-07 | 2008-06-15 | Weber Hydraulik Gmbh | Fluidzylinder-anordnung |
JP4933862B2 (ja) * | 2006-08-24 | 2012-05-16 | 北都建機サービス株式会社 | 油圧駆動装置 |
DE102009052531A1 (de) * | 2009-11-11 | 2011-05-12 | Hoerbiger Automatisierungstechnik Holding Gmbh | Maschinenpresse |
DE102010061840B4 (de) | 2010-06-14 | 2020-01-16 | Sms Group Gmbh | Kolben-Zylindereinheit als schaltbarer Stufen-Zylinder |
DE102010043168A1 (de) * | 2010-10-29 | 2012-05-03 | Metso Paper, Inc. | Druckspeicherfüllverfahren für ein Fluidsystem |
DE102011108256A1 (de) * | 2011-07-22 | 2013-01-24 | Rheinisch-Westfälische Technische Hochschule Aachen | Hydraulische Antriebsvorrichtung und Austauschvorrichtung für hydraulische Antriebe |
CN103357671B (zh) * | 2012-03-26 | 2015-06-17 | 苏州泰克诺机电有限公司 | 压力流量闭环可调的液压系统 |
DE102012015118B3 (de) * | 2012-04-17 | 2013-10-10 | Hoerbiger Automatisierungstechnik Holding Gmbh | Maschinenpresse |
US9234587B2 (en) * | 2012-05-23 | 2016-01-12 | Caterpillar Global Mining Llc | Multi-capacity cylinder |
DE102012020581A1 (de) * | 2012-10-22 | 2014-04-24 | Robert Bosch Gmbh | Hydraulische Schaltung für eine hydraulische Achse und eine hydraulische Achse |
DE102013222472A1 (de) | 2013-11-06 | 2015-05-07 | Robert Bosch Gmbh | Hydraulischer Druckübersetzer |
WO2015117240A1 (en) * | 2014-02-06 | 2015-08-13 | Ensign Drilling Partnership | Hydraulic multi-displacement hoisting cylinder system |
DE102014005352B4 (de) * | 2014-04-11 | 2016-03-10 | Hoerbiger Automatisierungstechnik Holding Gmbh | Maschinenpresse |
CN104132023B (zh) * | 2014-07-02 | 2016-08-10 | 中国人民解放军国防科学技术大学 | 可控变截面液压缸及其液压控制系统和控制方法 |
DE102014110484A1 (de) * | 2014-07-24 | 2016-01-28 | Jungheinrich Aktiengesellschaft | Flurförderzeug mit einem elektrischen Hydraulikpumpenaggregat |
US10851811B2 (en) | 2015-09-10 | 2020-12-01 | Festo Se & Co. Kg | Fluid system and process valve |
DE102016205973A1 (de) * | 2016-04-11 | 2017-10-12 | Sms Group Gmbh | Hydraulikzylinder |
JP2019015348A (ja) * | 2017-07-07 | 2019-01-31 | 東京エレクトロン株式会社 | ガスシリンダ |
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DE3836371A1 (de) * | 1988-10-26 | 1990-05-03 | Schloemann Siemag Ag | Hydraulische antriebsvorrichtung fuer schlingenheber |
EP0499826A1 (de) * | 1991-02-16 | 1992-08-26 | Krupp Maschinentechnik Gesellschaft Mit Beschränkter Haftung | Antriebseinrichtung für ein Abbruchwerkzeug |
US5353683A (en) * | 1993-07-20 | 1994-10-11 | Snitgen Joseph D | Pneumatic transformer |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
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US2869237A (en) * | 1956-09-17 | 1959-01-20 | Joseph M Berge | Trammel bar compass |
DE1091435B (de) * | 1959-03-18 | 1960-10-20 | Toussaint & Hess Gmbh | Hydraulischer Kolbenantrieb |
US3452397A (en) * | 1965-10-07 | 1969-07-01 | Rockford Machine Tool Co | Hydraulic actuator for an injection molding machine |
JPS5215627B1 (de) * | 1971-07-10 | 1977-05-02 | ||
SU561812A1 (ru) * | 1975-09-08 | 1977-06-15 | Всесоюзный Научно-Исследовательский Институт Резинотехнического Машиностроения | Система управлени скоростью движени гидроцилиндра |
DE2726246C3 (de) * | 1977-06-10 | 1981-11-12 | Jungheinrich Unternehmensverwaltung Kg, 2000 Hamburg | Hydraulikanlage für den Hubantrieb eines Hubladers |
DE3003689A1 (de) * | 1980-02-01 | 1981-08-06 | Leo Gottwald KG, 4000 Düsseldorf | Teleskopausleger fuer krane |
DD227058A1 (de) * | 1984-10-08 | 1985-09-11 | Warnke Umformtech Veb K | Anordnung zum regeln fuer steuerbare pneumatikkissen |
DE3735123A1 (de) * | 1987-10-16 | 1989-06-29 | Hartmann & Laemmle | Hydraulische antriebsvorrichtung |
US4833971A (en) * | 1988-03-09 | 1989-05-30 | Kubik Philip A | Self-regulated hydraulic control system |
US5090296A (en) * | 1991-01-09 | 1992-02-25 | Todd Motion Controls Inc. | Piston assembly and method |
SK368091A3 (en) * | 1991-12-04 | 1994-05-11 | Frantisek Krnavek | Device for potential energy recuperation of working device of building or earth machine |
-
1995
- 1995-11-24 DE DE19543876A patent/DE19543876A1/de not_active Withdrawn
-
1996
- 1996-10-11 EP EP96945157A patent/EP0862697B1/de not_active Expired - Lifetime
- 1996-10-11 DE DE59605729T patent/DE59605729D1/de not_active Expired - Lifetime
- 1996-10-11 WO PCT/DE1996/001934 patent/WO1997020146A1/de active IP Right Grant
- 1996-10-11 US US09/068,402 patent/US6145307A/en not_active Expired - Fee Related
Patent Citations (6)
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DE2220180A1 (de) * | 1972-04-25 | 1973-11-08 | Geb Maier Gisela Bieber | Hydraulischer zylinder ohne durchgehende kolbenstange mit gleichen vorschubund rueckzugflaechen, sowie mit schnellgangeinrichtung |
JPS5484182A (en) * | 1977-12-16 | 1979-07-04 | Nec Corp | Oil hydraulic pressure apparatus |
EP0327666A1 (de) * | 1988-02-02 | 1989-08-16 | Josef Nusser | Hydraulischer Antrieb |
DE3836371A1 (de) * | 1988-10-26 | 1990-05-03 | Schloemann Siemag Ag | Hydraulische antriebsvorrichtung fuer schlingenheber |
EP0499826A1 (de) * | 1991-02-16 | 1992-08-26 | Krupp Maschinentechnik Gesellschaft Mit Beschränkter Haftung | Antriebseinrichtung für ein Abbruchwerkzeug |
US5353683A (en) * | 1993-07-20 | 1994-10-11 | Snitgen Joseph D | Pneumatic transformer |
Non-Patent Citations (1)
Title |
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PATENT ABSTRACTS OF JAPAN vol. 003, no. 108 (M - 072) 11 September 1979 (1979-09-11) * |
Also Published As
Publication number | Publication date |
---|---|
EP0862697B1 (de) | 2000-08-09 |
US6145307A (en) | 2000-11-14 |
DE59605729D1 (de) | 2000-09-14 |
EP0862697A1 (de) | 1998-09-09 |
DE19543876A1 (de) | 1997-05-28 |
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