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EP2420681A2 - Entraînement linéaire hydraulique - Google Patents

Entraînement linéaire hydraulique Download PDF

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Publication number
EP2420681A2
EP2420681A2 EP11006709A EP11006709A EP2420681A2 EP 2420681 A2 EP2420681 A2 EP 2420681A2 EP 11006709 A EP11006709 A EP 11006709A EP 11006709 A EP11006709 A EP 11006709A EP 2420681 A2 EP2420681 A2 EP 2420681A2
Authority
EP
European Patent Office
Prior art keywords
pressure
pressure chamber
linear drive
drive according
hydraulic
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
EP11006709A
Other languages
German (de)
English (en)
Other versions
EP2420681A3 (fr
EP2420681B1 (fr
Inventor
Bastian Beckmann
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 EP2420681A2 publication Critical patent/EP2420681A2/fr
Publication of EP2420681A3 publication Critical patent/EP2420681A3/fr
Application granted granted Critical
Publication of EP2420681B1 publication Critical patent/EP2420681B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • 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
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • 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
    • F15B2211/20561—Type of pump reversible
    • 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
    • F15B2211/27—Directional control by means of the pressure source
    • 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
    • F15B2211/30505—Non-return valves, i.e. check 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
    • F15B2211/30—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
    • F15B2211/3058—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 having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
    • 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
    • F15B2211/70—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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/785—Compensation of the difference in flow rate in closed fluid circuits using differential actuators

Definitions

  • the invention relates to a hydraulic linear drive according to the preamble of patent claim 1.
  • Such hydraulic linear drives can be used, for example, for actuating a press ram of a press, wherein a pressing tool is closed via the linear drive, for example, at rapid traverse, and the actual pressing operation is then carried out with comparatively great force in a so-called "power stroke". After the pressing process, the press die is then moved back into its basic position in rapid reverse direction.
  • linear drives are also used in other applications, such as stamping, machine tools, production lines, etc.
  • the pressure medium connection to the variable displacement pump, to the hydraulic accumulator and to the tank is controlled by a valve arrangement, in which case for the power stroke, the active surfaces of the first and the third pressure chamber with the pump pressure and the effective effective direction in the opposite direction of the second pressure chamber with tank pressure is applied, the connection to the hydraulic accumulator is then shut off.
  • a separate charge pump is assigned in the hydraulic accumulator, so that it is always charged to a predetermined level.
  • the invention has for its object to provide a hydraulic linear drive, which has a relatively simple structure and allows an optimized in terms of energy control.
  • the hydraulic linear drive has a hydraulic cylinder, which is designed with three of each active area limited pressure chambers, which can be acted upon by a hydraulic machine, preferably a pump and a valve assembly with high pressure (pump) or a low pressure source, for example, with tank pressure to the hydraulic cylinder to move in rapid traverse or in a power stroke in one direction and in rapid traverse or in the power stroke in the other direction.
  • the hydraulic motor is designed with a variable-speed drive, wherein the area ratios of the active surfaces are tuned so that the drive operates at about the same speed range in rapid traverse and in the power stroke.
  • the hydraulic machine can be designed with a constant delivery / displacement volume. However, in principle also suitable for a four-quadrant operation designed hydraulic machines in which a reversal of direction is possible.
  • the valve assembly has a directional control valve which connects in one position a pressure port of the hydraulic machine via a working line with a first pressure chamber and a second pressure chamber via a further working line with the low pressure source, for example the tank. In a further position, the directional control valve blocks a connection of the second pressure chamber to the low-pressure source.
  • a control valve is arranged downstream of the directional control valve, which connects in one position the first pressure chamber with the second pressure chamber acting in the opposite direction.
  • the third pressure chamber may be connected to the low-pressure source / tank via a suction line with a non-return valve opening in the direction of the third pressure chamber.
  • the low-pressure source is associated with a storage valve which connects in one position the low-pressure source with a suction side of the hydraulic machine and in another position the former working line in the region between the directional control valve and the control valve with the low-pressure source.
  • the first pressure chamber is preferably designed with a larger effective area than the second pressure space acting in the opposite direction.
  • the second effective area is designed slightly smaller than the third effective area.
  • the hydraulic linear drive can be carried out particularly advantageously as a press drive or as the closing axis of an injection molding machine.
  • the inventive concept can be used wherever force and speed are needed at different times.
  • the hydraulic cylinder is designed with a piston having a piston hollow rod into which a rod of the hydraulic cylinder is immersed, so that the first pressure chamber is limited by this and an inner end face of the piston piston rod, which is supplied through the rod with pressure medium.
  • a piston hollow rod-side annular end face of the piston bounds the second pressure chamber and a rod-side annular end face facing away from the third pressure chamber in sections.
  • FIG. 1 Linear drive shown, for example, in the stamping or forming technology, such as servo presses, tube and wire bending machines, press brakes, punching and nibbling machines, stamping and forming machines, Saugtransfer- or compact suction presses, tire presses, tire building machines, Vulkanisierpressen, drawing presses, transfer and transfer presses, Extruders, bending centers, forging presses, scrap presses, injection molding machines, blow molding or powder metal presses are used.
  • stamping or forming technology such as servo presses, tube and wire bending machines, press brakes, punching and nibbling machines, stamping and forming machines, Saugtransfer- or compact suction presses, tire presses, tire building machines, Vulkanisierpressen, drawing presses, transfer and transfer presses, Extruders, bending centers, forging presses, scrap presses, injection molding machines, blow molding or powder metal presses are used.
  • the linear drive 1 has a hydraulic cylinder 2, which, as will be explained in more detail below, with three pressure chambers 4, 6, 8 is executed.
  • the pressure medium supply via a hydraulic machine 10, preferably a constant displacement pump, which is driven by a variable-speed motor 12.
  • a suction connection of the pump is connected via a low-pressure line 14 to a low-pressure source 16, for example a hydraulic accumulator or a tank.
  • a pressure port of the hydraulic machine 10 is connected to a pressure line 18, which leads to the input port of a directional control valve 20.
  • this is designed as a 4/2-way switching valve, wherein in a basic position shown (a), the pressure line 18 is connected to a supply line 22, which in turn leads to the input terminal of a control valve 24, which also as 4/2 ways -Switch valve is executed.
  • this connects the supply line 22 with a working line 26, via which the first pressure chamber 4 is supplied with pressure medium.
  • a further connection of the control valve 24 is connected via a regeneration line 28 to a further working line 30, which is connected on the one hand to an output connection of the directional control valve 20 and on the other hand to the second pressure chamber 6.
  • the regeneration line 28 is connected to the working line 26 and shut off in the position (b) to the first pressure chamber 4 out.
  • the connection of the return line to the other working line 30 is shut off.
  • the directional control valve 20 has a return port, the is connected via a return line 32 to the low pressure line 14.
  • the pressure medium connection between this return line 32 and the other working line 30 is interrupted. By switching to the position marked with (b) this pressure medium connection is opened.
  • the third pressure chamber 8 is connected to a further output port of the control valve 24 via a third working line 34 shown only for illustrative reasons.
  • This working line 34 can also be combined with the suction line 36, which will be explained below.
  • this third working line 34 is shut off to the supply line 22, the regeneration line 28 and the working line 26 out.
  • the third working line 34 is connected to the working line 26 and the supply line 22.
  • the third pressure chamber 8 is additionally connected via a suction line 36 with a non-return valve 38 open to the third pressure chamber 8 with the low-pressure line 14.
  • a storage valve 40 which is designed in the embodiment as a 3/2-way switching valve.
  • the low-pressure source 16 In its illustrated basic position (a), the low-pressure source 16 is connected to the low-pressure line 14.
  • the accumulator valve 40 By switching the accumulator valve 40, the low-pressure source 16 is connected to a line 42 opening into the supply line 22 and the connection to the low-pressure line 14 is blocked.
  • the line 42 is shut off in the position (a) of the storage valve 40 to the low pressure source 16 out.
  • the hydraulic cylinder 2 is designed with a piston 44 which has a piston hollow rod 46 into which a rod 50 supported on the cylinder bottom 48 dips, so that an inner end surface 52 of the piston hollow rod 46 and the end face of the rod 50 define the first pressure chamber 4. Its pressure is supplied via a extending through the rod 50 through channel 54 which is connected to the working line 26.
  • a piston rod-side annular end face 56 of the piston 54 bounded in the axial direction of the second, penetrated by the piston hollow rod 46 pressure chamber 6 and another, rod-side annular end face 58 bounded by the rod 50 third pressure chamber 8.
  • the effective surfaces of these pressure chambers are in FIG. 2 marked with the designations A1, A2, A3.
  • the pressure chamber 6 is as shown FIG. 1 explained, connected to the other working line 30 and the pressure chamber 8 to the third working line 34 and 36.
  • the hydraulic machine is to promote a volume flow O P at a predetermined pressure, which is to act on a comparatively small, effective in the extension direction surface of the hydraulic cylinder 2, so that with a comparatively low flow - And associated low drive power - a high extension speed of the hydraulic cylinder 2 can be effected.
  • the directional control valve 20 and the control valve 24 are brought to their (a) marked positions.
  • the storage valve 40 is also connected to the position (a), so that sucked from the low pressure source 16 via the hydraulic machine 10 pressure medium and is conveyed via the supply line 22, the working line 26 and the channel 54 in the first pressure chamber 4.
  • the regeneration line 28 is connected to the working line 26, so that the two pressure chambers 4, 6 are connected to each other.
  • the third pressure chamber 8 is in rapid traverse via the suction line 36 and the non-return valve 48 opening to the pressure chamber 8 with the Low pressure line 14 and thus connected to the low pressure source 16.
  • the pressure chamber 4 with the active surface A 1 a pressure medium flow is supplied via the hydraulic machine 10, so that the piston hollow rod 46 extends in the arrow direction.
  • the pressure medium is ejected from the decreasing second pressure chamber 6 and summed via the regeneration line 28 to the funded by the hydraulic machine 10 pressure medium flow rate Q P.
  • the third pressure chamber 8 increases, so that pressure medium is sucked in via the check valve 48 from the low-pressure source 16.
  • the piston hollow rod 46 thus extends at a comparatively high speed at a relatively low pressure medium volume flow.
  • the volume flows Q 1 , Q 2 are calculated from the product of the extension speed x with the respective effective area A 1 , A 2 .
  • the delivery volume flow Q p of the hydraulic machine can be calculated from the product of the speed n of the drive 12 with the delivery / displacement volume V of the hydraulic machine 10, so that the pressure medium volume flow Q p, EIL in rapid traverse according to the equations: A p .
  • EIL x A 1 - A 2 V ⁇ n
  • EIL x ⁇ EIL ⁇ A 1 - A 2 calculated.
  • the piston hollow rod 46 is extended with comparatively low speed and great force.
  • the hydraulic machine 10 according to FIG. 3 promote a pressure medium volume Q p , force on the largest possible effective area to produce the desired large force.
  • the control valve 24 and the control valve 20 are switched to their switching positions (b).
  • the storage valve 40 remains in position (a). Accordingly, the first pressure chamber 4 is supplied with a comparatively large effective area A 1 with pressure medium.
  • the acting in the same direction effective area A 3 of the third pressure chamber 8 is also acted upon by the pressure of the hydraulic machine 10.
  • the directional control valve 20 and the control valve 24 each remain in their switching position (b), so that the hydraulic machine 10 promotes the pressure medium volume flow Q p , Eil in the second pressure chamber 6 acting in the retraction direction.
  • the two acting in the opposite direction Pressure chambers 4, 8 are connected via the directional control valve 20 and the control valve 24 and the switched to its switching position (b) storage valve 40 to the low pressure source 16, so that the pressure medium from these pressure chambers 4, 8 to the low pressure source 16 or to the suction side of the hydraulic machine 10 out can flow - the hydraulic cylinder 2 is retracted at high speed and low power.
  • the active surfaces A 1 . A 2 , A 3 designed and interconnected with each other, that the engine 12 in both the power stroke and rapid traverse (back and forth) with approximately the same speed or with approximately the same torque, in which case by suitable interconnection, the desired traversing speed x or Force (px A) is achieved.
  • FIG. 5 shows the linear drive during the power stroke - just as in the embodiment described above, the directional control valve 20 and the control valve 24 are adjusted in their switching positions (a), so that the active surfaces A 1 , A 3 are acted upon by the pressure at the output of the hydraulic machine 10.
  • the second pressure chamber 6 is connected via the further working line 30, the directional control valve 20, the return line 32 and the low pressure line 14 to the low pressure source 16, so that the pressure medium from the third pressure chamber 6 can be pushed out.
  • a hydraulic linear drive with a running with three pressure chambers hydraulic cylinder the active surfaces are coordinated so that in a rapid traverse and in a power stroke, a drive of the hydraulic cylinder with pressure medium supplying hydraulic machine operates in about the same speed / torque range.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Actuator (AREA)
EP11006709.7A 2010-08-18 2011-08-17 Entraînement linéaire hydraulique Active EP2420681B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102010034610A DE102010034610A1 (de) 2010-08-18 2010-08-18 Hydraulischer Linearantrieb

Publications (3)

Publication Number Publication Date
EP2420681A2 true EP2420681A2 (fr) 2012-02-22
EP2420681A3 EP2420681A3 (fr) 2014-09-24
EP2420681B1 EP2420681B1 (fr) 2020-01-08

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP11006709.7A Active EP2420681B1 (fr) 2010-08-18 2011-08-17 Entraînement linéaire hydraulique

Country Status (2)

Country Link
EP (1) EP2420681B1 (fr)
DE (1) DE102010034610A1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2015031364A (ja) * 2013-08-05 2015-02-16 住友重機械工業株式会社 ショベル
JP2015031365A (ja) * 2013-08-05 2015-02-16 住友重機械工業株式会社 ショベル
WO2016008151A1 (fr) * 2014-07-18 2016-01-21 Norgren, Inc. Cylindre de moulage par soufflage avec étirage et procédé associé
CN105452678A (zh) * 2013-08-05 2016-03-30 住友重机械工业株式会社 挖土机
EP3109485A1 (fr) * 2015-06-25 2016-12-28 Robert Bosch Gmbh Systeme hydraulique destine a l'alimentation en fluide sous pression d'un verin hydraulique comprenant trois surfaces actives separees alimentees en fluide sous pression et procede de fonctionnement dudit systeme hydraulique
WO2017140499A1 (fr) * 2016-02-16 2017-08-24 Sms Group Gmbh Cylindre à pas constant pour installations d'extrusion
CN107243774A (zh) * 2017-05-19 2017-10-13 深圳市睿格晟设备有限公司 一种改良吸屑机
DE102018203367A1 (de) 2018-03-07 2019-09-12 Robert Bosch Gmbh Hydrostatischer Linearantrieb
EP3705733A1 (fr) * 2019-03-04 2020-09-09 Wacker Neuson Linz GmbH Entraînement linéaire à circuit hydraulique fermé

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5522212A (en) 1994-12-21 1996-06-04 Kubik; Philip A. Rod equal displacement cylinder in a rapid transfer and feed system
DE102008039011A1 (de) 2008-08-21 2010-02-25 MAE Maschinen- und Apparatebau Götzen GmbH & Co. KG Druckspeicherlose hydraulische Antriebsanordnung sowie Verfahren zum druckspeicherlosen hydraulischen Antreiben eines Verbrauchers

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL8105929A (nl) * 1981-12-31 1983-07-18 Hydraudyne Bv Zuiger/cilinder eenheid.
DE102004027849A1 (de) * 2004-06-08 2006-01-05 Bosch Rexroth Aktiengesellschaft Antriebseinheit

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5522212A (en) 1994-12-21 1996-06-04 Kubik; Philip A. Rod equal displacement cylinder in a rapid transfer and feed system
DE102008039011A1 (de) 2008-08-21 2010-02-25 MAE Maschinen- und Apparatebau Götzen GmbH & Co. KG Druckspeicherlose hydraulische Antriebsanordnung sowie Verfahren zum druckspeicherlosen hydraulischen Antreiben eines Verbrauchers

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10100847B2 (en) 2013-08-05 2018-10-16 Sumitomo Heavy Industries, Ltd. Shovel
JP2015031365A (ja) * 2013-08-05 2015-02-16 住友重機械工業株式会社 ショベル
CN105452678A (zh) * 2013-08-05 2016-03-30 住友重机械工业株式会社 挖土机
EP3032112A4 (fr) * 2013-08-05 2016-08-31 Sumitomo Heavy Industries Pelle
JP2015031364A (ja) * 2013-08-05 2015-02-16 住友重機械工業株式会社 ショベル
WO2016008151A1 (fr) * 2014-07-18 2016-01-21 Norgren, Inc. Cylindre de moulage par soufflage avec étirage et procédé associé
EP3109485A1 (fr) * 2015-06-25 2016-12-28 Robert Bosch Gmbh Systeme hydraulique destine a l'alimentation en fluide sous pression d'un verin hydraulique comprenant trois surfaces actives separees alimentees en fluide sous pression et procede de fonctionnement dudit systeme hydraulique
US10670052B2 (en) 2016-02-16 2020-06-02 Sms Group Gmbh Synchronizing cylinder for extruder
WO2017140499A1 (fr) * 2016-02-16 2017-08-24 Sms Group Gmbh Cylindre à pas constant pour installations d'extrusion
CN108603521A (zh) * 2016-02-16 2018-09-28 Sms集团有限公司 用于连续压制设备的同步缸
CN107243774B (zh) * 2017-05-19 2019-11-08 深圳市睿格晟设备有限公司 一种改良吸屑机
CN107243774A (zh) * 2017-05-19 2017-10-13 深圳市睿格晟设备有限公司 一种改良吸屑机
DE102018203367A1 (de) 2018-03-07 2019-09-12 Robert Bosch Gmbh Hydrostatischer Linearantrieb
EP3705733A1 (fr) * 2019-03-04 2020-09-09 Wacker Neuson Linz GmbH Entraînement linéaire à circuit hydraulique fermé

Also Published As

Publication number Publication date
DE102010034610A1 (de) 2012-02-23
EP2420681A3 (fr) 2014-09-24
EP2420681B1 (fr) 2020-01-08

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