EP3178581A1 - Cylindre à haute fréquence - Google Patents

Cylindre à haute fréquence Download PDF

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Publication number
EP3178581A1
EP3178581A1 EP16002610.0A EP16002610A EP3178581A1 EP 3178581 A1 EP3178581 A1 EP 3178581A1 EP 16002610 A EP16002610 A EP 16002610A EP 3178581 A1 EP3178581 A1 EP 3178581A1
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EP
European Patent Office
Prior art keywords
piston
cylinder
pressure
accumulator
extension
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
EP16002610.0A
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German (de)
English (en)
Other versions
EP3178581B1 (fr
Inventor
Ulrich Keller
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Individual
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Individual
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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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/26—Supply reservoir or sump assemblies
    • F15B1/265—Supply reservoir or sump assemblies with pressurised main reservoir
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
    • B30B1/32—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by plungers under fluid 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1476—Special return means
    • 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/26—Locking mechanisms
    • 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F15B15/223—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having a piston with a piston extension or piston recess which completely seals the main fluid outlet as the piston approaches its end 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
    • F15B2211/625—Accumulators

Definitions

  • the invention relates to a high-frequency cylinder according to claims 1 to 8 From the patent literature Schnellhubzylinder said hydraulic cylinders are known, which are designed for the generation of rapid rapid movements in hydraulic presses. Examples: DE102005047995B4 . DE 000019642635A1 or DE 000002127605C3 , Fast rapid movements are for example desired in idle strokes of machines such as presses and are referred to as quick-stroke or rapid traverse cylinder. They move the press ram in the idle stroke much faster than it would be possible with the area far larger working cylinder. The oil of the working cylinder is sucked in only with negative pressure. They have the same structure as usual working cylinders.
  • hydraulic cylinders are also referred to as rapid traverse or quick-lift cylinders when conventional hydraulic cylinders receive an oil feed via storage or servo valves ( DE102007010426B4 ).
  • the dynamics can also be improved ( DE000003215795A1 ).
  • Such known cylinders can be used for example in test benches, where it is required to accelerate a test object to a higher speed.
  • Another field of application is the rapid supply and removal of parts in production processes. For certain applications, however, much higher speeds are desired with high cylinder forces.
  • various processes of manufacturing processing of products in question in which highest speeds are desired.
  • the object of the present invention is therefore to provide an extremely fast and yet reliable and very compact high-frequency drive with the highest operating speeds, for example for high-speed cutting (HGSS) or forging.
  • a hydraulic cylinder is designed so that the piston can extend at extremely high speeds.
  • the return stroke of the piston should take place in the shortest possible time in order to enable the highest number of deliveries.
  • stroke rates of 1000 rpm are possible and that a limitation mainly occurs through the switching times of valves.
  • the usual number of deliveries of hydraulic presses are far exceeded.
  • the limitation is eliminated by switching times of valves for even higher stroke rates.
  • the extremely fast extending piston can directly actuate a working element or serve as a drive for another drive, for example, designed for a hydraulic cylinder as a pressure booster. This object is achieved by the invention according to claims 1 to 8.
  • Fig. 1 describes the design of the high-frequency cylinder according to the invention.
  • the control ring 33 forms with the lower part of the collar 5 a sealing surface 34 which shields the pressure prevailing in the cylinder chamber 23 against the control chamber 38.
  • the control chamber 38 is relieved via the control valve 32 to tank.
  • the control ring 33 is acted upon on its underside with the pressure prevailing in the cylinder chamber 23 pressure. On its upper side, it is partially relieved of pressure via a small paragraph to the control chamber 38 and the pressure drop across the sealing surface 34 between the cylinder chamber 23 and the control chamber 38.
  • the upper annular surface of the collar 5 is fully loaded with the pressure prevailing in the cylinder chamber 23, while the pressure axially opposite lower collar surface is only partially acted upon by the pressure prevailing in the cylinder chamber 23 pressure.
  • the piston is locked.
  • the gas storage space formed between the parts 17 and 7, a gas, for example nitrogen was introduced before the pressure build-up in the cylinder chamber 23.
  • the storage piston 17 sat on the spacer tube 24.
  • the accumulator piston 17 was moved upwards and reduces the volume of the gas storage space to 1/3.
  • the piston should always reduce its energy externally in one operation. Should it happen due to an incorrect setting that no external energy reduction takes place, the collar 5 of the piston 1 enters the Oldämpfungsraum 20 a. By entering into the formed on the oil damping chamber 20 slope energy of the piston is reduced there. The spring-back of the accumulator piston 17 in the direction of the gas storage space 21 supports the energy reduction. As a rule, however, the collar 5 of the piston 1 comes to a standstill beforehand due to the external operation.
  • the piston 1 has an upper piston portion 2 and a lower piston portion 3. These form the differential area 4, via which the return stroke is realized by means of pressurization. When extending the piston oil is displaced by the differential surface 4 and must be as low flow can flow out, otherwise it would hinder the expansion of the piston with the construction of a flow pressure.
  • Fig. 2 shows the fast and reliable control by means of a rotary valve.
  • a rotary valve is for example from the Scriptures DE 10 2012 024 642 A1 known. It is able to realize a valve control at highest frequencies up to 2000 / min.
  • a stator 40 and a rotor 39 are provided.
  • the rotor 39 has the recesses a to d. These connect depending on the rotation angle of the rotor 39, the terminals 29 and 30 of the high-frequency cylinder with pump and tank according to the present rotation angle.
  • Fig. 2a and Fig. 2b represent in the rotary valve successively arranged cuts.
  • the rotor may be mechanically coupled to the drive of a feed unit not shown via a direct shaft connection or a transmission. In this way it is ensured that the movement of the piston 1 runs absolutely synchronously with the feed at the highest stroke rates of the high-frequency cylinder.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
EP16002610.0A 2015-12-12 2016-12-08 Cylindre à haute fréquence Active EP3178581B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102015016149.0A DE102015016149A1 (de) 2015-12-12 2015-12-12 Hochfrequenzzylinder

Publications (2)

Publication Number Publication Date
EP3178581A1 true EP3178581A1 (fr) 2017-06-14
EP3178581B1 EP3178581B1 (fr) 2019-11-27

Family

ID=57542663

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16002610.0A Active EP3178581B1 (fr) 2015-12-12 2016-12-08 Cylindre à haute fréquence

Country Status (2)

Country Link
EP (1) EP3178581B1 (fr)
DE (1) DE102015016149A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112176997A (zh) * 2020-09-16 2021-01-05 林清辉 一种高频振动式打桩机构

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2127605C3 (de) 1971-06-03 1980-01-24 Shigeo Chosi Chiba Ando (Japan) Automatische hydraulische Schnelläuferpresse
DE3215795A1 (de) 1982-04-28 1983-11-17 Festo-Maschinenfabrik Gottlieb Stoll, 7300 Esslingen Hochgeschwindigkeitszylinder
DE4233115A1 (de) * 1992-10-02 1994-04-07 Keller Ulrich Hydraulikaggregat
DE19602390A1 (de) * 1995-01-28 1996-08-01 Ulrich Keller Arbeitszylinder
DE19642635A1 (de) 1996-03-28 1997-10-02 Horst Baltschun Feinschneidpresse mit hydraulisch gekoppeltem Ringzacken- und Gegenhalterzylinder
FR2894303A1 (fr) * 2005-12-02 2007-06-08 Pommier S C E B P Sa Verin hydraulique a amortissement
DE102007018066A1 (de) 2007-04-17 2008-10-30 Grimm, Georg, Dipl.-Ing. Vorrichtungen und Verfahren zum dynamischen Umformen unter Verwendung eines Impulsübertragungskolbens
DE102007010426B4 (de) 2007-03-01 2008-11-13 Ortwin Prof. Dr.-Ing. Hahn Prüfvorrichtung für Proben unter Stoßbelastung
DE102005047995B4 (de) 2004-10-13 2009-03-12 Engel Austria Gmbh Verfahren und Einrichtung zum Betrieb einer Spritzgießeinrichtung
DE102011109066A1 (de) * 2011-07-28 2013-01-31 Thomas Sauer Arbeitsmaschine mit verbesserter, energierückgewinnender Stelleinheit
DE102012019386A1 (de) 2012-10-02 2014-04-03 Institut für Umformtechnik der mittelständischen Wirtschaft GmbH Vorrichtungen für Hochgeschwindigkeitsverfahren (Hochgeschwindigkeitsumformen oder Hochgeschwindigkeits-Scherschneiden) auf konventionellen Maschinen und Verfahren zur fertigfallenden Herstellung von Umformteilen mit der Kombination von Arbeitsgängen mit
DE102012024642A1 (de) 2012-12-15 2014-06-18 Ulrich Keller Hochfrequenzkompaktventil mit Eigenantrieb zur Erzeugung hydraulischer Schwingungen und praktisch reibfreier Axiallagerung eines rotierenden Teiles

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3990351A (en) * 1972-03-10 1976-11-09 Atlas Copco Aktiebolag Pneumatic impact device
DE2845924C2 (de) * 1978-10-21 1984-04-26 Schwelmer Eisenwerk Müller & Co GmbH, 5830 Schwelm Schnellstanzpresse
JPS6182011A (ja) * 1984-09-27 1986-04-25 Shimadzu Corp 油圧シリンダ
DE3913866A1 (de) * 1989-04-27 1990-10-31 Krupp Maschinentechnik Hydraulisches schlagwerk

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2127605C3 (de) 1971-06-03 1980-01-24 Shigeo Chosi Chiba Ando (Japan) Automatische hydraulische Schnelläuferpresse
DE3215795A1 (de) 1982-04-28 1983-11-17 Festo-Maschinenfabrik Gottlieb Stoll, 7300 Esslingen Hochgeschwindigkeitszylinder
DE4233115A1 (de) * 1992-10-02 1994-04-07 Keller Ulrich Hydraulikaggregat
DE19602390A1 (de) * 1995-01-28 1996-08-01 Ulrich Keller Arbeitszylinder
DE19642635A1 (de) 1996-03-28 1997-10-02 Horst Baltschun Feinschneidpresse mit hydraulisch gekoppeltem Ringzacken- und Gegenhalterzylinder
DE102005047995B4 (de) 2004-10-13 2009-03-12 Engel Austria Gmbh Verfahren und Einrichtung zum Betrieb einer Spritzgießeinrichtung
FR2894303A1 (fr) * 2005-12-02 2007-06-08 Pommier S C E B P Sa Verin hydraulique a amortissement
DE102007010426B4 (de) 2007-03-01 2008-11-13 Ortwin Prof. Dr.-Ing. Hahn Prüfvorrichtung für Proben unter Stoßbelastung
DE102007018066A1 (de) 2007-04-17 2008-10-30 Grimm, Georg, Dipl.-Ing. Vorrichtungen und Verfahren zum dynamischen Umformen unter Verwendung eines Impulsübertragungskolbens
DE102011109066A1 (de) * 2011-07-28 2013-01-31 Thomas Sauer Arbeitsmaschine mit verbesserter, energierückgewinnender Stelleinheit
DE102012019386A1 (de) 2012-10-02 2014-04-03 Institut für Umformtechnik der mittelständischen Wirtschaft GmbH Vorrichtungen für Hochgeschwindigkeitsverfahren (Hochgeschwindigkeitsumformen oder Hochgeschwindigkeits-Scherschneiden) auf konventionellen Maschinen und Verfahren zur fertigfallenden Herstellung von Umformteilen mit der Kombination von Arbeitsgängen mit
DE102012024642A1 (de) 2012-12-15 2014-06-18 Ulrich Keller Hochfrequenzkompaktventil mit Eigenantrieb zur Erzeugung hydraulischer Schwingungen und praktisch reibfreier Axiallagerung eines rotierenden Teiles

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112176997A (zh) * 2020-09-16 2021-01-05 林清辉 一种高频振动式打桩机构

Also Published As

Publication number Publication date
EP3178581B1 (fr) 2019-11-27
DE102015016149A1 (de) 2017-06-14

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