EP1763638A1 - Pressure-medium cylinder with pressure-translation - Google Patents

Pressure-medium cylinder with pressure-translation

Info

Publication number
EP1763638A1
EP1763638A1 EP05769977A EP05769977A EP1763638A1 EP 1763638 A1 EP1763638 A1 EP 1763638A1 EP 05769977 A EP05769977 A EP 05769977A EP 05769977 A EP05769977 A EP 05769977A EP 1763638 A1 EP1763638 A1 EP 1763638A1
Authority
EP
European Patent Office
Prior art keywords
cylinder
pressure
piston
pressure medium
cylinders
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
EP05769977A
Other languages
German (de)
French (fr)
Other versions
EP1763638B1 (en
Inventor
Rudolf Langeder
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.)
Primetals Technologies Austria GmbH
Original Assignee
Voest Alpine Industrienlagenbau 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 Voest Alpine Industrienlagenbau GmbH filed Critical Voest Alpine Industrienlagenbau GmbH
Publication of EP1763638A1 publication Critical patent/EP1763638A1/en
Application granted granted Critical
Publication of EP1763638B1 publication Critical patent/EP1763638B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F15B11/032—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters
    • F15B11/0325—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters the fluid-pressure converter increasing the working force after an approach stroke
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/16—Adjusting or positioning rolls
    • B21B31/20—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis
    • B21B31/32—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis by liquid pressure, e.g. hydromechanical adjusting
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
    • B21B37/58—Roll-force control; Roll-gap control
    • B21B37/62—Roll-force control; Roll-gap control by control of a hydraulic adjusting device
    • 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
    • F15B15/28—Means for indicating the position, e.g. end of stroke
    • F15B15/2815—Position sensing, i.e. means for continuous measurement of position, e.g. LVDT
    • 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
    • F15B2211/214—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being hydrotransformers
    • 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
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration

Definitions

  • the subject invention relates to a pressure medium cylinder with pressure intensification, wherein two separate cylinders are arranged in the pressure medium cylinder, in each of which a piston is arranged and the piston of the first cylinder has a Kol ⁇ rod, which is operatively ver ⁇ connected with the second cylinder to increase the pressure and a use of such a pressure medium cylinder as adjusting cylinder in a roll stand, as well as a method for operating and controlling such Druck ⁇ central cylinder.
  • Pressure cylinder must be able to apply high forces for certain applications, for example in rolling stands, and / or be able to position exactly.
  • a pressure medium cylinder for example a hydraulic cylinder
  • a piston having a large cross section and / or the pressure medium cylinder must be supplied with pressurized fluid under high pressure.
  • the pressure medium cylinder is very large and in the second case, a high cost must be operated for the pressure medium system.
  • a large amount of pressure medium has to be moved, as a result of which the dynamics of such cylinders, that is to say the time to perform adjusting movements of the cylinder, suffer.
  • WO 02/053920 A2 shows a hydraulic or hydropneumatic pressure booster which combines a low-pressure cylinder and a working cylinder in a housing. In such a pressure booster, however, the two pistons can not be controlled independently of one another. Only the low-pressure cylinder, which transmits the movement to a working piston, can be activated. However, this also limits the range of motion of the working cylinder, or it again requires large volumes and dimensions, which in turn would impair the dynamics.
  • the pressure medium for the working cylinder is not supplied from the outside, but is included in Druck ⁇ translator, which can lead to problems with leakage losses and the pressure medium must be refilled regularly. It is therefore an object of the present invention to provide a hydraulic cylinder which has a compact design, generates high contact forces and has high dynamics.
  • the cylinders can be actuated independently of each other.
  • both cylinders are controlled independently, a large range of motion with a relatively small cylinder volume and thus small size can be realized.
  • a cylinder may e.g. roughly prepositioned and the second cylinder can be used for fine positioning under high pressure and high dynamics was ⁇ .
  • such a pressure medium cylinder can also be operated and controlled particularly flexibly and simply by using one cylinder for coarse positioning and a second cylinder for fine positioning under high pressure and low response times.
  • the pressure medium cylinder is also equipped with a position measuring system with which the position of at least one of the two cylinder pistons can be detected, since the actual position of a piston that can be detected can be used directly for a control or control.
  • FIG. 1 shows a section through a pressure medium cylinder according to the invention
  • FIG. 2 shows a schematic representation of a rolling stand with a pressure medium cylinder according to the invention.
  • the pressure medium cylinder here a hydraulic cylinder 1, according to FIG. 1, has a housing 2 in which two cylinders, a pressure transmission cylinder 5 and a positioning cylinder 8, are arranged.
  • a pressure transmission cylinder 5 In the two cylinders 5, 8 is in each case a piston, a Druckschreib GmbHs ⁇ piston 3 and a Anstellkolben 6, respectively.
  • the pressure booster cylinder 5 and the adjusting cylinder 8 are hydraulically separated from each other and can be controlled independently of each other via their own supply line 9, 11 and their own Ablei ⁇ device 10, 12 for hydraulic fluid.
  • the Anstellkolben 6 has a Anstellkolbenstange 7 which is guided through the housing 2 of the hydraulic cylinder 1 to the outside and, for. can be used as any actuating means or can be associated with such.
  • the adjusting piston 6 can also have a depression 15 in the size of the cross section of the pressure-transmitting piston rod 4, as indicated in FIG. 1, to produce a contact, e.g. in the event of a malfunction, between the pressure transmission piston rod 4 and Anstellkolben 6 and a possible damage to avoid the same.
  • the pressure booster piston 3 is connected to a pressure booster piston rod 4, which is guided in a dividing wall formed by a part of the housing 2 between the pressure transmission cylinder 5 and the adjusting cylinder 8 and guided therethrough and thus operatively connected to the positioning cylinder 8 and to the hydraulic fluid lumen of the adjusting cylinder 8 is in communication.
  • the pressure booster piston 3 and the pressure booster piston rod 4 are here dimensioned such that the pressure-transmitting piston rod 4 does not dive into the positioning cylinder space in a topmost position of the pressure booster piston 3.
  • a piston-side pressure is thus translated in the ratio of the cross sections of the pressure booster piston 3 and the pressure booster piston rod 4, so enlarged, on the Anstellkolben 6 piston side thus acts thus increased pressure.
  • the Anstellkolben 6 is further connected to a encoder armature 13, which here by the pressure booster piston rod 4, the pressure booster piston 3 and the housing of the hydraulic cylinder 1 performed and with a suitable Wegmesssys ⁇ system 14, e.g. a well-known electrical or optical system connected.
  • a suitable Wegmesssys ⁇ system 14 e.g. a well-known electrical or optical system connected.
  • the displacement measuring system 14 may e.g. with a control of the hydraulic cylinder 1 and / or the control of a device actuated by the hydraulic cylinder 1, such as e.g. a roll of a rolling mill, be linked, e.g. as actual value transmitter.
  • Both pistons 3, 6 are on the piston side, ie at the supply lines 9, 11, with a pressurized, For example, a pressure of 290 bar, connected hydraulic system. Both cylinders can therefore be supplied by the same hydraulic system. Piston rod side, so at the discharge lines 10, 12, is at both cylinders 5, 8, a constant, reduced pressure, for example, a pressure of about 50 bar, to. The actuation of the cylinders 5, 8 can take place as known by means of known servo valves arranged in the inlet 9, 11 and / or outlet 10, 12.
  • the adjusting valve 6 of the adjusting piston 6 with the adjusting piston rod 7 is moved to a predetermined position via the servo valve. This position is transmitted via the encoder armature 13, which is fixedly connected to the Anstellkolben 6 and passed through the pressure booster piston 3, über ⁇ to the displacement measuring system 14 über ⁇ .
  • the displacement measuring system 14 may be linked to a suitable control.
  • the pressure booster piston 3 is at the time of positioning the Anstellkol ⁇ bens 6 in its uppermost position and is not active.
  • pressure booster piston 3 and Anstellkol ⁇ ben 6 now immersed the pressure booster piston rod 4, whose diameter is in a certain ratio to the pressure translation piston diameter, in the Zylinder ⁇ space of the Anstellkolbens 6, which has the consequence that there is a by the ratio Pressure booster piston cross section to pressure booster piston rod cross section multiplied hydraulic pressure builds up.
  • the control path of the intensifier multiplies by the same ratio.
  • the actuating piston 6 can be actuated and moved by a multiplied pressure by activating the pressure-compensating cylinder 5.
  • the hydraulic cylinder 1 according to the invention with a hydraulic system of relatively low pressure and small dimensions to impinge the Anstell ⁇ piston 6 with a x times the pressure of the hydraulic system.
  • the gear ratio is about 1 to 4, i. From the 290 bar piston pressure of the pressure booster, 1160 bar would result in the adjusting cylinder 8.
  • Such a hydraulic cylinder 1 can be used particularly advantageously as a setting cylinder 28 in a roll stand, as shown schematically in Fig. 2.
  • the rolling stand 20 here consists of two work rolls 22 and two backup rolls 21 and there is a rolled strip 23, which passes through between the two work rolls 22 rolled.
  • Such arrangements are well known and need not be explained in detail.
  • an inventive hydraulic cylinder 1 is arranged, the adjusting cylinder 7 actuates a here only indicated adjusting device 24.
  • a control unit 25 receives measurement data from the displacement measuring system 14 and controls the hydraulic cylinder 1.
  • the control unit 25 can control even further parts of the system or even receive measurement data from further sensors 26, as indicated in FIG. 2.
  • control unit 25 can also be linked to a higher-level control 27, for example a system control.
  • the hydraulic cylinder 1 now regulates by the control unit 25 as described above in accordance with the specifications and under control of the pressure booster cylinder 5 with sufficient reaction times, all from the different rolling forces resultingie nenden roll gap changes.
  • measured values required with the sensors 26 can be detected and supplied to the control unit 25.
  • 20 ways in the order of magnitude of between 1 and 5 mm are to be controlled in a roll stand. After the threaded strip 23 has been removed from the rolling stand 20, the pressure-transmitting piston 3 is immediately moved back into the uppermost position and the control is transferred again to the setting cylinder 8 of the hydraulic cylinder 1. With its renewed positioning, the next cycle begins.
  • the hydraulic cylinder 1 Due to the small volume of the two cylinders 5, 8, the hydraulic cylinder 1 still has sufficiently high response times with still very high achievable pressures. At the same time, the controllability of the hydraulic cylinder 1 is not impaired by the possibility of controlling the two cylinders 5, 8 independently of one another.
  • the use of such a pressure cylinder 1 thus lends itself wherever high forces are required in a small footprint, in addition to rolling stands, for example. without restriction also in forging presses or edger stands.
  • a pressure medium cylinder according to the invention is described above using the example of a hydraulic cylinder 1, but of course any other suitable pressure means, e.g. Air or gas for a pneumatic cylinder, are used, with little functional changes could result without functional limitations.
  • any other suitable pressure means e.g. Air or gas for a pneumatic cylinder, are used, with little functional changes could result without functional limitations.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
  • Color Printing (AREA)
  • Pens And Brushes (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Control Of Fluid Pressure (AREA)
  • Lubricants (AREA)

Abstract

For many applications, high adjustment forces are required for pressure-medium cylinders. The dynamics of said cylinders are often impaired as a result of large piston cross-sections and cylinder volumes and/or the pressure medium has to be supplied at very high pressure. The invention relates to a pressure-medium cylinder offering short reaction times, high adjustment forces and a compact structure. This is achieved by virtue of the fact that two independently controllable cylinders (5,8) are arranged in the pressure-medium cylinder (1).

Description

DRUCKMITTELZYLINDER MIT DRUCKUBERSETZUNG PRESSURE RELEASE PRESSURE CYLINDER
Die gegenständliche Erfindung betrifft einen Druckmittelzylinder mit Druckübersetzung, wobei im Druckmittelzylinder zwei voneinander getrennte Zylinder angeordnet sind, in denen jeweils ein Kolben angeordnet ist und der Kolben des ersten Zylinders eine Kol¬ benstange aufweist, die mit dem zweiten Zylinder zur Druckerhöhung wirkungsmäßig ver¬ bunden ist und eine Verwendung eines solchen Druckmittelzylinders als Anstellzylinder in einem Walzgerüst, sowie ein Verfahren zum Betreiben und Regeln eines solchen Druck¬ mittelzylinders.The subject invention relates to a pressure medium cylinder with pressure intensification, wherein two separate cylinders are arranged in the pressure medium cylinder, in each of which a piston is arranged and the piston of the first cylinder has a Kol¬ rod, which is operatively ver¬ connected with the second cylinder to increase the pressure and a use of such a pressure medium cylinder as adjusting cylinder in a roll stand, as well as a method for operating and controlling such Druck¬ central cylinder.
Druckmittelzylinder müssen für bestimmte Anwendungen, z.B. in Walzgerüsten, hohe Kräfte aufbringen können und/oder genau positionsregelbar sein. Dazu kann ein Druck¬ mittelzylinder, z.B. ein Hydraulikzylinder, mit einem Kolben mit großem Querschnitt vorge¬ sehen werden und/oder der Druckmittelzylinder muss mit unter hohem Druck stehenden Druckmittel versorgt werden. Im ersten Fall wird der Druckmittelzylinder sehr groß und im zweiten Fall muss für das Druckmittelsystem ein hoher Aufwand betrieben werden. Dar¬ über hinaus muss bei großen Zylindern eine große Menge von Druckmittel bewegt wer¬ den, wodurch die Dynamik solcher Zylinder, also die Zeit um Stellbewegungen des Zylin¬ ders durchzuführen, leidet. Aus der DE 36 30 725 A geht nun z.B. eine Druckübersetzung hervor, um den Druck in der Hydraulikzuleitung zu einem Hydraulikzylinder zu erhöhen. Der Druckübersetzer ar¬ beitet hier jedoch pneumatisch, was zwei unterschiedliche Versorgungsmedien und die damit verbundenen Anlagen notwendig macht. Die oben beschriebenen Probleme lassen sich mit solchen Druckübersetzern jedoch nicht lösen. Die WO 02/053920 A2 zeigt einen hydraulischen bzw. hydropneumatischen Drucküber- setzer, der einen Niederdruckzylinder und einen Arbeitszylinder in einem Gehäuse verei¬ nigt. Bei einem solchen Druckübersetzer können die beiden Kolben jedoch nicht unab¬ hängig voneinander angesteuert werden. Ansteuerbar ist lediglich der Niederdruckzylin¬ der, der die Bewegung an einen Arbeitskolben überträgt. Damit ist aber auch der Bewe¬ gungsspielraum des Arbeitszylinders eingeschränkt, oder man benötigt wieder große Vo- lumina und Abmessungen, wodurch wiederum die Dynamik leiden würde. Außerdem wird das Druckmittel für den Arbeitszylinder nicht von außen zugeführt, sondern ist im Druck¬ übersetzer eingeschlossen, was zu Problemen mit Leckageverlusten führen kann und das Druckmittel regelmäßig nachgefüllt werden muss. Es ist daher eine Aufgabe der vorliegenden Erfindung einen Hydraulikzylinder anzugeben, der kompakt aufgebaut ist, hohe Anstellkräfte erzeugt und eine hohe Dynamik aufweist.Pressure cylinder must be able to apply high forces for certain applications, for example in rolling stands, and / or be able to position exactly. For this purpose, a pressure medium cylinder, for example a hydraulic cylinder, can be provided with a piston having a large cross section and / or the pressure medium cylinder must be supplied with pressurized fluid under high pressure. In the first case, the pressure medium cylinder is very large and in the second case, a high cost must be operated for the pressure medium system. In addition, in the case of large cylinders, a large amount of pressure medium has to be moved, as a result of which the dynamics of such cylinders, that is to say the time to perform adjusting movements of the cylinder, suffer. From DE 36 30 725 A is now, for example, a pressure translation out to increase the pressure in the hydraulic supply to a hydraulic cylinder. However, the pressure booster works here pneumatically, which makes two different supply media and the associated systems necessary. However, the problems described above can not be solved with such pressure translators. WO 02/053920 A2 shows a hydraulic or hydropneumatic pressure booster which combines a low-pressure cylinder and a working cylinder in a housing. In such a pressure booster, however, the two pistons can not be controlled independently of one another. Only the low-pressure cylinder, which transmits the movement to a working piston, can be activated. However, this also limits the range of motion of the working cylinder, or it again requires large volumes and dimensions, which in turn would impair the dynamics. In addition, the pressure medium for the working cylinder is not supplied from the outside, but is included in Druck¬ translator, which can lead to problems with leakage losses and the pressure medium must be refilled regularly. It is therefore an object of the present invention to provide a hydraulic cylinder which has a compact design, generates high contact forces and has high dynamics.
Diese Aufgabe wird durch die Erfindung gelöst, indem die Zylinder unabhängig voneinan¬ der ansteuerbar sind. Dadurch dass beide Zylindern unabhängig voneinander ansteuerbar sind, kann ein großer Bewegungsspielraum mit relativ geringem Zylindervolumen und damit geringer Baugröße realisiert werden. Ein Zylinder kann z.B. grob vorpositioniert werden und der zweite Zylin¬ der kann zur Feinpositionierung unter hohem Druck und hoher Dynamik verwendet wer¬ den. Diese Maßnahmen erlauben somit eine wesentliche Reduktion der Zylinderbaugrö- ße, ermöglicht einen Druckmittelzylinder auch als Langhubausführung auszuführen, z.B. für die Integration in einen Walzenständer, und bringt wesentliche Gewichts- und Ferti¬ gungskosteneinsparungen mit sich.This object is achieved by the invention in that the cylinders can be actuated independently of each other. The fact that both cylinders are controlled independently, a large range of motion with a relatively small cylinder volume and thus small size can be realized. A cylinder may e.g. roughly prepositioned and the second cylinder can be used for fine positioning under high pressure and high dynamics wer¬. These measures thus allow a substantial reduction in the cylinder size, also making it possible to design a pressure cylinder as a long-stroke version, e.g. for integration into a roll stand, and brings about significant weight and manufac turing cost savings.
Durch die beiden unabhängig voneinander ansteuerbaren Zylinder lässt sich ein solcher Druckmittelzylinder auch besonders flexibel und einfach betreiben und ansteuern, indem ein Zylinder zur Grobpositionierung und ein zweiter Zylinder zur Feinpositionierung unter hohen Druck und geringen Ansprechzeiten verwendet wird.By means of the two independently controllable cylinders, such a pressure medium cylinder can also be operated and controlled particularly flexibly and simply by using one cylinder for coarse positioning and a second cylinder for fine positioning under high pressure and low response times.
Besonders vorteilhaft ist der Druckmittelzylinder auch mit einem Wegmesssystem ausge¬ stattet, mit dem die Position zumindest eines der beiden Zylinderkolbens erfasst werden kann, da die so erfassbare Istposition eines Kolben direkt für eine Regelung oder Steue- rung verwendet werden kann.Particularly advantageously, the pressure medium cylinder is also equipped with a position measuring system with which the position of at least one of the two cylinder pistons can be detected, since the actual position of a piston that can be detected can be used directly for a control or control.
Die vorliegende Erfindung wird im Nachfolgenden anhand der beispielhaften, schemati¬ schen und nicht einschränkenden Figuren 1 und 2 beschrieben. Dabei zeigtThe present invention will be described below with reference to the exemplary, schematic and non-limiting Figures 1 and 2. It shows
Fig. 1 einen Schnitt durch einen erfindungsgemäßen Druckmittelzylinder und Fig. 2 eine schematische Darstellung eines Walzgerüsts mit einem erfindungsge- mäßen Druckmittelzylinder.1 shows a section through a pressure medium cylinder according to the invention, and FIG. 2 shows a schematic representation of a rolling stand with a pressure medium cylinder according to the invention.
Der Druckmittelzylinder, hier ein Hydraulikzylinder 1 , nach Fig. 1 weist ein Gehäuse 2 auf in dem zwei Zylinder, ein Druckübersetzungszylinder 5 und ein Anstellzylinder 8, ange¬ ordnet sind. In den beiden Zylindern 5, 8 ist jeweils ein Kolben, ein Druckübersetzungs¬ kolben 3 und ein Anstellkolben 6, angeordnet. Auf die genaue konstruktive Ausgestaltung der Zylinder 5, 8 und der zugehörigen Kolben 3, 6 kann hier verzichtet werden, da solche hydraulische Zylinder hinlänglich bekannt sind und in vielfältigster Weise ausgeführt sein können.The pressure medium cylinder, here a hydraulic cylinder 1, according to FIG. 1, has a housing 2 in which two cylinders, a pressure transmission cylinder 5 and a positioning cylinder 8, are arranged. In the two cylinders 5, 8 is in each case a piston, a Druckübersetzungs¬ piston 3 and a Anstellkolben 6, respectively. On the exact structural design of the cylinder 5, 8 and the associated piston 3, 6 can be omitted here, since such hydraulic cylinders are well known and executed in many ways can.
Der Druckübersetzungszylinder 5 und der Anstellzylinder 8 sind dabei hydraulisch von¬ einander getrennt und können über jeweils eine eigene Zuleitung 9, 11 und eigene Ablei¬ tung 10, 12 für Hydraulikflüssigkeit unabhängig voneinander angesteuert werden. Der Anstellkolben 6 weist eine Anstellkolbenstange 7 auf, die durch das Gehäuse 2 des Hydraulikzylinders 1 nach außen geführt ist und z.B. als beliebiges Betätigungsmittel ver¬ wendet werden kann oder mit einem solchen in Verbindung stehen kann. Der Anstellkol¬ ben 6 kann auch eine Vertiefung 15 in der Größe des Querschnitts der Drücküberset- zungskolbenstange 4 aufweisen, wie in Fig. 1 angedeutet, um einen Kontakt, z.B. im Falle einer Fehlfunktion, zwischen der Drückübersetzungskolbenstange 4 und Anstellkolben 6 und einer eventuellen Beschädigung derselben zu vermeiden.The pressure booster cylinder 5 and the adjusting cylinder 8 are hydraulically separated from each other and can be controlled independently of each other via their own supply line 9, 11 and their own Ablei¬ device 10, 12 for hydraulic fluid. The Anstellkolben 6 has a Anstellkolbenstange 7 which is guided through the housing 2 of the hydraulic cylinder 1 to the outside and, for. can be used as any actuating means or can be associated with such. The adjusting piston 6 can also have a depression 15 in the size of the cross section of the pressure-transmitting piston rod 4, as indicated in FIG. 1, to produce a contact, e.g. in the event of a malfunction, between the pressure transmission piston rod 4 and Anstellkolben 6 and a possible damage to avoid the same.
Der Druckübersetzungskolben 3 ist mit einer Druckübersetzungskolbenstange 4 verbun¬ den, die in einer von einem Teil des Gehäuses 2 gebildeten Trennwand zwischen Druck¬ übersetzungszylinder 5 und Anstellzylinder 8 geführt und durch diese hindurchgeführt ist und somit wirkungsmäßig mit dem Anstellzylinder 8 bzw. mit dem Hydraulikflüssigkeitsvo¬ lumen des Anstellzylinders 8 in Verbindung steht. Der Druckübersetzungskolben 3 und die Druckübersetzungskolbenstange 4 ist hier so dimensioniert, dass die Drucküberset¬ zungskolbenstange 4 in einer obersten Position des Druckübersetzungskolbens 3 nicht in den Anstellzylinderraum eintaucht. Ein kolbenseitiger Druck wird folglich im Verhältnis der Querschnitte des Druckübersetzungskolbens 3 und der Druckübersetzungskolbenstange 4 übersetzt, also vergrößert, auf den Anstellkolben 6 wirkt kolbenseitig somit der derart vergrößerte Druck.The pressure booster piston 3 is connected to a pressure booster piston rod 4, which is guided in a dividing wall formed by a part of the housing 2 between the pressure transmission cylinder 5 and the adjusting cylinder 8 and guided therethrough and thus operatively connected to the positioning cylinder 8 and to the hydraulic fluid lumen of the adjusting cylinder 8 is in communication. The pressure booster piston 3 and the pressure booster piston rod 4 are here dimensioned such that the pressure-transmitting piston rod 4 does not dive into the positioning cylinder space in a topmost position of the pressure booster piston 3. A piston-side pressure is thus translated in the ratio of the cross sections of the pressure booster piston 3 and the pressure booster piston rod 4, so enlarged, on the Anstellkolben 6 piston side thus acts thus increased pressure.
Der Anstellkolben 6 ist weiters mit einem Messgebergestänge 13 verbunden, das hier durch die Druckübersetzungskolbenstange 4, den Druckübersetzungskolben 3 und das Gehäuse des Hydraulikzylinders 1 durchgeführt und mit einem geeigneten Wegmesssys¬ tem 14, z.B. ein hinlänglich bekanntes elektrisches oder optisches System, verbunden ist. Es ist jedoch selbstverständlich, dass auch ein beliebiges anderes Wegmesssystem 14 oder eine beliebige andere Wegmessanordnung als die hier beschriebene vorgesehen sein könnte. Das Wegmesssystem 14 kann z.B. mit einer Regelung des Hydraulikzylin- ders 1 und/oder der Regelung einer vom Hydraulikzylinder 1 betätigten Vorrichtung, wie z.B. einer Walze eines Walzgerüsts, verknüpft sein, z.B. als Istwertgeber.The Anstellkolben 6 is further connected to a encoder armature 13, which here by the pressure booster piston rod 4, the pressure booster piston 3 and the housing of the hydraulic cylinder 1 performed and with a suitable Wegmesssys¬ system 14, e.g. a well-known electrical or optical system connected. However, it is to be understood that any other displacement measuring system 14 or any other displacement measuring arrangement could be provided as described herein. The displacement measuring system 14 may e.g. with a control of the hydraulic cylinder 1 and / or the control of a device actuated by the hydraulic cylinder 1, such as e.g. a roll of a rolling mill, be linked, e.g. as actual value transmitter.
Die Funktion des erfindungsgemäßen Hydraulikzylinders 1 wird nachfolgend beispielhaft beschrieben.The function of the hydraulic cylinder 1 according to the invention will be described below by way of example.
Beide Kolben 3, 6 sind kolbenseitig, also an den Zuleitungen 9, 11 , mit einem unter Druck, z.B. ein Druck von 290 bar, stehenden Hydrauliksystem verbunden. Beide Zylinder kön¬ nen also vom selben Hydrauliksystem versorgt werden. Kolbenstangenseitig, also an den Ableitungen 10, 12, steht bei beiden Zylindern 5, 8 ein konstanter, reduzierter Druck, z.B. ein Druck von ca. 50 bar, an. Die Ansteuerung der Zylinder 5, 8 kann wie hinlänglich be- kannt mittels in der Zu- 9, 11 und/oder Ableitung 10, 12 angeordneten bekannten Servo- ventilen erfolgen.Both pistons 3, 6 are on the piston side, ie at the supply lines 9, 11, with a pressurized, For example, a pressure of 290 bar, connected hydraulic system. Both cylinders can therefore be supplied by the same hydraulic system. Piston rod side, so at the discharge lines 10, 12, is at both cylinders 5, 8, a constant, reduced pressure, for example, a pressure of about 50 bar, to. The actuation of the cylinders 5, 8 can take place as known by means of known servo valves arranged in the inlet 9, 11 and / or outlet 10, 12.
Als erster Schritt wird über das Servoventil des Anstellzylinders 8 der Anstellkolben 6 mit der Anstellkolbenstange 7 in eine vorgegebene Position gefahren. Diese Position wird über das Messgebergestänge 13, welches mit dem Anstellkolben 6 fix verbunden ist und durch den Druckübersetzerkolben 3 hindurchgeführt ist, an das Wegmesssystem 14 über¬ tragen. Das Wegmesssystem 14 kann mit einer geeigneten Regelung verknüpft sein. Der Druckübersetzerkolben 3 befindet sich zum Zeitpunkt der Positionierung des Anstellkol¬ bens 6 in seiner obersten Lage und ist nicht aktiv. Nach der Positionierung des Anstellkol¬ bens 6 und damit der Anstellkolbenstange 7 durch die Ansteuerung des Anstellzylinders 8 wird dessen Hydraulikzuleitung 11 z.B. mittels eines sperrbaren Ventils vom Hydrauliksys¬ tem getrennt und die Regelfunktion des Hydraulikzylinders 1 wird nun vom Drucküberset¬ zerzylinder 5 über dessen Servoventil übernommen.As a first step, the adjusting valve 6 of the adjusting piston 6 with the adjusting piston rod 7 is moved to a predetermined position via the servo valve. This position is transmitted via the encoder armature 13, which is fixedly connected to the Anstellkolben 6 and passed through the pressure booster piston 3, über¬ to the displacement measuring system 14 über¬. The displacement measuring system 14 may be linked to a suitable control. The pressure booster piston 3 is at the time of positioning the Anstellkol¬ bens 6 in its uppermost position and is not active. After the positioning of the Anstellkol¬ bens 6 and thus the Anstellkolbenstange 7 by the control of the Anstellzylinders 8 whose hydraulic feed line 11, for. separated by Hydrauliksys¬ system by means of a lockable valve and the control function of the hydraulic cylinder 1 is now taken over by the Drucküberset¬ cylinder 5 via the servo valve.
Durch die erfindungsgemäße Anordnung von Druckübersetzungskolben 3 und Anstellkol¬ ben 6 taucht nun die Druckübersetzungskolbenstange 4, deren Durchmesser in einem bestimmten Verhältnis zum Druckübersetzungskolbendurchmesser steht, in den Zylinder¬ raum des Anstellkolbens 6 ein, was zur Folge hat, dass sich dort ein um das Verhältnis Druckübersetzungskolbenquerschnitt zu Druckübersetzungskolbenstangenquerschnitt multiplizierter Hydraulikdruck aufbaut. Der Regelweg des Druckübersetzers multipliziert sich dabei um das gleiche Verhältnis. Somit kann durch Ansteuern des Drucküberset- zungszylinders 5 der Anstellkolben 6 mit einem multiplizierten Druck angesteuert und be¬ wegt werden. Es ist mit dem erfindungsgemäßen Hydraulikzylinder 1 also möglich mit einem Hydrauliksystem relativ geringen Druckes und geringer Dimensionen den Anstell¬ kolben 6 mit einem x-fachen des Druckes des Hydrauliksystems zu beaufschlagen. In diesem Beispiel beträgt das Übersetzungsverhältnis ungefähr 1 zu 4, d.h. aus den 290 bar Kolbendruck des Druckübersetzers würden sich 1160 bar im Anstellzylinder 8 erge¬ ben.Due to the inventive arrangement of pressure booster piston 3 and Anstellkol¬ ben 6 now immersed the pressure booster piston rod 4, whose diameter is in a certain ratio to the pressure translation piston diameter, in the Zylinder¬ space of the Anstellkolbens 6, which has the consequence that there is a by the ratio Pressure booster piston cross section to pressure booster piston rod cross section multiplied hydraulic pressure builds up. The control path of the intensifier multiplies by the same ratio. Thus, the actuating piston 6 can be actuated and moved by a multiplied pressure by activating the pressure-compensating cylinder 5. It is thus possible with the hydraulic cylinder 1 according to the invention with a hydraulic system of relatively low pressure and small dimensions to impinge the Anstell¬ piston 6 with a x times the pressure of the hydraulic system. In this example, the gear ratio is about 1 to 4, i. From the 290 bar piston pressure of the pressure booster, 1160 bar would result in the adjusting cylinder 8.
Ein solcher Hydraulikzylinder 1 kann besonders vorteilhaft als Anstellzylinder 28 in einem Walzgerüst angewendet werden, wie in Fig. 2 schematisch dargestellt. Das Walzgerüst 20 besteht hier aus zwei Arbeitswalzen 22 und zwei Stützwalzen 21 und es wird ein Walzband 23, das zwischen den beiden Arbeitswalzen 22 durchläuft gewalzt. Solche Anordnungen sind hinlänglich bekannt und müssen nicht näher erläutert werden. Am Walzgerüst 20 ist ein erfindungsgemäßer Hydraulikzylinder 1 angeordnet, dessen Anstellzylinder 7 eine hier nur angedeutete Anstelleinrichtung 24 betätigt. Eine Regelungseinheit 25 erhält vom Wegmesssystem 14 Messdaten und steuert den Hydraulikzylinder 1 an. Die Regelungseinheit 25 kann noch weitere Anlagenteile steuern bzw. noch von weiteren Sensoren 26 Messdaten erhalten, wie in Fig. 2 angedeutet. E- benso kann die Regelungseinheit 25 auch mit einer übergeordneten Regelung 27, z.B. eine Anlagenregelung, verknüpft sein. Der Hydraulikzylinder 1 regelt nun durch die Regelungseinheit 25 wie oben beschrieben entsprechend den Vorgaben und unter Ansteuerung des Druckübersetzungszylinders 5 mit ausreichenden Reaktionszeiten, alle aus den unterschiedlichen Walzkräften resultie¬ renden Walzspaltveränderungen aus. Dazu können mit den Sensoren 26 benötigte Messwerte erfasst und der Regelungseinheit 25 zugeführt werden. Erfahrungsgemäß sind in einem Walzgerüst 20 Wege in der Größenordnung zwischen 1 und 5mm auszuregeln. Nach dem Ausfädeln des Walzbandes 23 aus dem Walzgerüst 20 wird der Drucküberset¬ zungskolben 3 sofort wieder in die oberste Lage gefahren und die Regelung wieder an den Anstellzylinder 8 des Hydraulikzylinders 1 übergeben. Mit dessen erneuter Positionie¬ rung beginnt der nächste Zyklus.Such a hydraulic cylinder 1 can be used particularly advantageously as a setting cylinder 28 in a roll stand, as shown schematically in Fig. 2. The rolling stand 20 here consists of two work rolls 22 and two backup rolls 21 and there is a rolled strip 23, which passes through between the two work rolls 22 rolled. Such arrangements are well known and need not be explained in detail. On the rolling stand 20, an inventive hydraulic cylinder 1 is arranged, the adjusting cylinder 7 actuates a here only indicated adjusting device 24. A control unit 25 receives measurement data from the displacement measuring system 14 and controls the hydraulic cylinder 1. The control unit 25 can control even further parts of the system or even receive measurement data from further sensors 26, as indicated in FIG. 2. Likewise, the control unit 25 can also be linked to a higher-level control 27, for example a system control. The hydraulic cylinder 1 now regulates by the control unit 25 as described above in accordance with the specifications and under control of the pressure booster cylinder 5 with sufficient reaction times, all from the different rolling forces resultingie nenden roll gap changes. For this purpose, measured values required with the sensors 26 can be detected and supplied to the control unit 25. Experience has shown that 20 ways in the order of magnitude of between 1 and 5 mm are to be controlled in a roll stand. After the threaded strip 23 has been removed from the rolling stand 20, the pressure-transmitting piston 3 is immediately moved back into the uppermost position and the control is transferred again to the setting cylinder 8 of the hydraulic cylinder 1. With its renewed positioning, the next cycle begins.
Es wäre aber selbstverständlich auch denkbar, beide Zylinder 5, 8 gleichzeitig anzusteu- ern, also gleichzeitig mit Hydraulikflüssigkeit zu beaufschlagen, falls es eine Anwendung erfordert.Of course, it would also be conceivable to simultaneously actuate both cylinders 5, 8, ie to apply hydraulic fluid at the same time, if it requires an application.
Durch die geringen Volumen der beiden Zylinder 5, 8 weist der Hydraulikzylinder 1 noch genügend hohe Ansprechzeiten bei trotzdem sehr hohen erreichbaren Drücken auf. Gleichzeitig wird durch die Möglichkeit, die beiden Zylinder 5, 8 unabhängig voneinander anzusteuern, die Regelbarkeit des Hydraulikzylinders 1 nicht beeinträchtigt. Der Einsatz eines solchen Druckmittelzylinders 1 bietet sich somit überall dort an, wo hohe Kräfte bei geringem Platzbedarf erforderlich sind, neben Walzgerüsten also z.B. ohne Einschrän¬ kung auch bei Schmiedepressen oder Stauchgerüsten.Due to the small volume of the two cylinders 5, 8, the hydraulic cylinder 1 still has sufficiently high response times with still very high achievable pressures. At the same time, the controllability of the hydraulic cylinder 1 is not impaired by the possibility of controlling the two cylinders 5, 8 independently of one another. The use of such a pressure cylinder 1 thus lends itself wherever high forces are required in a small footprint, in addition to rolling stands, for example. without restriction also in forging presses or edger stands.
Ein erfindungsgemäßer Druckmittelzylinder wird oben am Beispiel eines Hydraulikzylin- ders 1 beschrieben, allerdings könnte natürlich auch jedes andere geeignete Druckmittel, z.B. Luft oder Gas für einen Pneumatikzylinder, zum Einsatz kommen, wobei sich ohne funktionelle Einschränkungen geringe konstruktive Änderungen ergeben könnten. A pressure medium cylinder according to the invention is described above using the example of a hydraulic cylinder 1, but of course any other suitable pressure means, e.g. Air or gas for a pneumatic cylinder, are used, with little functional changes could result without functional limitations.

Claims

Patentansprüche claims
1. Druckmittelzylinder mit Druckübersetzung, vorzugsweise ein Hydraulik- oder Pneu¬ matikzylinder, wobei im Druckmittelzylinder (1 ) zwei voneinander getrennte Zylinder (5, 8) angeordnet sind, in denen jeweils ein Kolben (3, 6) angeordnet ist und der Kolben (3) des ersten Zylinders (5) eine Kolbenstange (4) aufweist, die mit dem zweiten Zylinder (8) zur Druckerhöhung wirkungsmäßig verbunden ist, dadurch gekennzeichnet, dass die Zylin¬ der (5, 8) unabhängig voneinander ansteuerbar sind.1. Pressure medium cylinder with pressure transmission, preferably a hydraulic or Pneu¬ matic cylinder, wherein in the pressure medium cylinder (1) two separate cylinders (5, 8) are arranged, in each of which a piston (3, 6) is arranged and the piston (3 ) of the first cylinder (5) has a piston rod (4) which is operatively connected to the second cylinder (8) for pressure increase, characterized in that the cylinders (5, 8) are independently controllable.
2. Druckmittelzylinder nach Anspruch 1 , dadurch gekennzeichnet, dass jeder Zylin- der (5, 8) eine eigene Zuleitung (9, 11 ) für Druckmittel und eine eigene Ableitung (10, 12) für Druckmittel aufweist.2. Pressure cylinder according to claim 1, characterized in that each cylinder (5, 8) has its own supply line (9, 11) for pressure medium and a separate discharge line (10, 12) for pressure medium.
3. Druckmittelzylinder nach einem Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Kolbenstange (4) des ersten Kolbens (3) eine kleinere Querschnittsfläche als der erste Kolben (3) aufweist.3. pressure cylinder according to one of claim 1 or 2, characterized in that the piston rod (4) of the first piston (3) has a smaller cross-sectional area than the first piston (3).
4. Druckmittelzylinder nach Anspruch 3, dadurch gekennzeichnet, dass die Kolben¬ stange (4) des ersten Kolbens (3) im Gehäuse (2) des Druckmittelzylinders (1 ) geführt angeordnet ist.4. pressure cylinder according to claim 3, characterized in that the Kolben¬ rod (4) of the first piston (3) in the housing (2) of the pressure medium cylinder (1) is guided out.
5. Druckmittelzylinder nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass der zweite Kolben (6) eine Kolbenstange (7) aufweist, die aus dem Druckmittelzylin- der (1 ) herausgeführt ist.5. Pressure medium cylinder according to one of claims 1 to 4, characterized in that the second piston (6) has a piston rod (7) which is led out of the Druckmittelzylin- the (1).
6. Druckmittelzylinder nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass am Druckmittelzylinder (1 ) ein Wegmesssystem (14) angeordnet ist, mit dem die Bewegung zumindest eines der beiden Kolben (3, 6), vorzugsweise des zweiten Kolbens (6), messbar ist.6. Pressure medium cylinder according to one of claims 1 to 5, characterized in that on the pressure medium cylinder (1) a displacement measuring system (14) is arranged, with which the movement of at least one of the two pistons (3, 6), preferably the second piston (6). , is measurable.
7. Druckmittelzylinder nach Anspruch 6, dadurch gekennzeichnet, dass ein Messge¬ bergestänge (13) vorgesehen ist, dass durch den ersten Kolben (3) und der ersten Kol¬ benstange (4) durchgeführt und mit einem Ende mit dem zweiten Kolben (6) bzw. mit dessen Kolbenstange (7) und mit dem anderen Ende mit dem Wegmesssystem (14) ver¬ bunden ist. 7. pressure cylinder according to claim 6, characterized in that a Meßge¬ bergestänge (13) is provided that by the first piston (3) and the first Kol¬ rod (4) performed and with one end to the second piston (6) or with the piston rod (7) and with the other end ver¬ connected to the displacement measuring system (14).
8. Verwendung des Druckmittelzylinders nach einem der Ansprüche 1 bis 7 als Anstellzylinder (28) einer Walze (21 ) eines Walzgerüsts (20).8. Use of the pressure cylinder according to one of claims 1 to 7 as adjusting cylinder (28) of a roller (21) of a roll stand (20).
9. Verwendung nach Anspruch 8, dadurch gekennzeichnet, dass die zweite Kolben¬ stange (7) mit einer Walze (21 ) oder einer Lagerung einer Walze (21 ) eines Walzgerüst (20) wirkungsmäßig verbunden ist.9. Use according to claim 8, characterized in that the second Kolben¬ rod (7) with a roller (21) or a bearing of a roller (21) of a roll stand (20) is operatively connected.
10. Verfahren zum Betreiben eines Druckmittelzylinders nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass die beiden Zylinder (5, 8) unabhängig voneinander mit Druckmittel beaufschlagt werden.10. A method for operating a pressure cylinder according to one of claims 1 to 7, characterized in that the two cylinders (5, 8) are acted upon independently of each other with pressure medium.
11. Verfahren nach Anspruch 10, dadurch gekennzeichnet, dass zuerst ein zweiter Kolben (7) eines zweiten Zylinders (8) durch Öffnen und/oder Schließen eines Ventils in der Druckmittelzuleitung (1 1 ) und/oder Druckmittelableitung (12) des zweiten Zylinders (8) in eine vorbestimmte Position bewegt wird und anschließend ein erster Kolben (3) eines ersten Zylinders (5) durch Öffnen und/oder Schließen eines Ventils in der Druckmittelzu¬ leitung (9) und/oder Druckmittelableitung (10) des ersten Zylinders (8) bewegt wird, wo- durch gleichzeitig auch der zweite Kolben (6) bewegt wird.11. The method according to claim 10, characterized in that first a second piston (7) of a second cylinder (8) by opening and / or closing a valve in the pressure medium supply line (1 1) and / or pressure medium discharge (12) of the second cylinder ( 8) is moved into a predetermined position and then a first piston (3) of a first cylinder (5) by opening and / or closing a valve in the Druckmittelzu¬ line (9) and / or pressure fluid discharge (10) of the first cylinder (8 ), which simultaneously moves the second piston (6) as well.
12. Verfahren zum Regeln eines Druckmittelzylinders nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass die beiden Zylinder (5, 8) unabhängig voneinander mit Druckmittel beaufschlagt werden.12. A method for controlling a pressure cylinder according to one of claims 1 to 7, characterized in that the two cylinders (5, 8) are acted upon independently of each other with pressure medium.
13. Verfahren nach Anspruch 12, dadurch gekennzeichnet, dass die Bewegung eines zweiten Kolbens (6) eines zweiten Zylinders (8) durch ein Wegmesssystem (14) erfasst wird und ein Ventil in der Druckmittelzuleitung (11) und/oder Druckmittelableitung (12) des zweiten Zylinders (8) derart angesteuert wird, dass der zweite Kolben (6) in eine vorbe¬ stimmte Position bewegt wird und anschließend die Bewegung des zweiten Kolbens (6) durch die Bewegung eines ersten Kolbens (3) eines ersten Zylinders (5) gesteuert wird, indem ein Ventil in der Druckmittelzuleitung (9) und/oder Druckmittelableitung (10) des ersten Zylinders (5) angesteuert werden.13. The method according to claim 12, characterized in that the movement of a second piston (6) of a second cylinder (8) by a position measuring system (14) is detected and a valve in the pressure medium supply line (11) and / or pressure medium discharge (12) of the second cylinder (8) is driven such that the second piston (6) is moved in a vorbe¬ certain position and then controlling the movement of the second piston (6) by the movement of a first piston (3) of a first cylinder (5) is controlled by a valve in the pressure medium supply line (9) and / or pressure medium discharge (10) of the first cylinder (5).
14. Verfahren nach einem der Ansprüche 10 bis 13, dadurch gekennzeichnet, dass der erste Kolben (3) während der Vorpositionierung des zweiten Kolbens (3) festgehalten wird. 14. The method according to any one of claims 10 to 13, characterized in that the first piston (3) during the pre-positioning of the second piston (3) is held.
15. Verfahren nach einem der Ansprüche 10 bis 14, dadurch gekennzeichnet, dass die Druckmittelzuleitung (11 ) und/oder Druckmittelableitung (12) des zweiten Zylinders (8) während der Bewegung des ersten Kolbens (3) abgesperrt wird. 15. The method according to any one of claims 10 to 14, characterized in that the pressure medium supply line (11) and / or pressure fluid discharge (12) of the second cylinder (8) during the movement of the first piston (3) is shut off.
EP05769977A 2004-07-02 2005-06-16 Pressure-medium cylinder with pressure-translation Not-in-force EP1763638B1 (en)

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AT0112304A AT500476B8 (en) 2004-07-02 2004-07-02 PRESSURE TRANSMISSION PRESSURE CYLINDER
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BRPI0512936A (en) 2008-04-15
JP4668991B2 (en) 2011-04-13
EP1763638B1 (en) 2008-05-07
RU2377446C2 (en) 2009-12-27
WO2006002772A1 (en) 2006-01-12
AT500476B1 (en) 2006-07-15
RU2007104052A (en) 2008-08-10
DE502005004029D1 (en) 2008-06-19
US20070289440A1 (en) 2007-12-20
CA2572486C (en) 2013-08-20
CA2572486A1 (en) 2006-01-12
SA05260195B1 (en) 2008-03-29
US7698893B2 (en) 2010-04-20
CN100532865C (en) 2009-08-26
UA84088C2 (en) 2008-09-10
JP2008504499A (en) 2008-02-14
ATE394599T1 (en) 2008-05-15
AT500476B8 (en) 2007-02-15
AT500476A1 (en) 2006-01-15
CN1989349A (en) 2007-06-27

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