[go: up one dir, main page]

EP1763638B1 - Pressure-medium cylinder with pressure-translation - Google Patents

Pressure-medium cylinder with pressure-translation Download PDF

Info

Publication number
EP1763638B1
EP1763638B1 EP05769977A EP05769977A EP1763638B1 EP 1763638 B1 EP1763638 B1 EP 1763638B1 EP 05769977 A EP05769977 A EP 05769977A EP 05769977 A EP05769977 A EP 05769977A EP 1763638 B1 EP1763638 B1 EP 1763638B1
Authority
EP
European Patent Office
Prior art keywords
pressure
cylinder
piston
medium
roll
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.)
Expired - Lifetime
Application number
EP05769977A
Other languages
German (de)
French (fr)
Other versions
EP1763638A1 (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
Siemens VAI Metals Technologies GmbH and Co
Siemens VAI Metals Technologies GmbH Austria
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 Siemens VAI Metals Technologies GmbH and Co, Siemens VAI Metals Technologies GmbH Austria filed Critical Siemens VAI Metals Technologies GmbH and Co
Publication of EP1763638A1 publication Critical patent/EP1763638A1/en
Application granted granted Critical
Publication of EP1763638B1 publication Critical patent/EP1763638B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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 cylinder with pressure transmission according to the preamble of claim 1, and a use of such a pressure cylinder as a positioning cylinder in a rolling stand.
  • Pressure cylinder must be able to apply high forces for certain applications, eg 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 must be moved, whereby the dynamics of such cylinders, so the time to perform actuator movements of the cylinder suffers.
  • the WO 02/053920 A2 shows a hydraulic or hydropneumatic pressure booster, which unites a low-pressure cylinder and a working cylinder in a housing.
  • the two pistons can not be controlled independently of each other.
  • the pressure medium for the working cylinder is not supplied from the outside, but is included in the pressure booster, which can lead to problems with leakage losses and the pressure medium must be replenished regularly.
  • a hydraulic cylinder according to the preamble of claim 1, refer to, in which a hydraulically driven pressure booster piston increases the hydraulic pressure on the working cylinder.
  • a displacement measuring system for controlling the piston positions is described. However, only one piston can be detected with respect to its position.
  • US 5,207,267 discloses a cylinder having two pistons operatively connected to each other. Each piston rod has its own measuring device, so that a more complex measuring device is necessary.
  • a cylinder may e.g. coarsely prepositioned and the second cylinder can be used for fine positioning under high pressure and high dynamics.
  • 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 piston can be detected, since the thus detectable actual position of a piston can be used directly for a control or control.
  • the pressure medium cylinder here a hydraulic cylinder 1, after Fig. 1 has a housing 2 in which two cylinders, a pressure booster cylinder 5 and a setting cylinder 8, are arranged.
  • a piston, a pressure booster piston 3 and an adjusting piston 6 are arranged in each of the two cylinders 5, 8, a piston, a pressure booster piston 3 and an adjusting piston 6 are arranged.
  • 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 own discharge 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 can be used for example as any actuator or can be associated with such.
  • the Anstellkolben 6 may also have a recess 15 in the size of the cross section of the pressure transmission piston rod 4, as in Fig. 1 indicated to avoid contact, for example in case of malfunction, between the pressure transmission piston rod 4 and Anstellkolben 6 and a possible damage to the same.
  • the pressure booster piston 3 is connected to a pressure booster piston rod 4, which is guided in a partition wall formed by a part of the housing 2 between the pressure booster cylinder 5 and adjusting cylinder 8 and through this and thus operatively connected to the adjusting cylinder 8 and with the hydraulic fluid volume of the Anstellzylinders 8 in connection stands.
  • the pressure booster piston 3 and the pressure booster piston rod 4 is dimensioned here such that the pressure booster piston rod 4 does not dive into the Anstellzylinderraum in an uppermost 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 translation piston rod 4, the pressure booster piston 3 and the housing of the hydraulic cylinder 1 and carried out with a suitable Wegmesssystem 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 operated 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 control of the cylinders 5, 8 can be done as well known by means arranged in the supply 9, 11 and / or discharge 10, 12 known servo valves.
  • the control path of the intensifier multiplies by the same ratio.
  • the pressure transmission cylinder 5 of the Anstellkolben 6 can be driven and moved with a multiplied pressure. 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 pressurize the Anstellkolben 6 with a x times the pressure of the hydraulic system.
  • the transmission ratio is about 1 to 4, ie 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 in Fig. 2 shown schematically.
  • 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.
  • 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 data from other sensors 26 as in Fig. 2 indicated.
  • the control unit 25 may 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 according to the specifications and under control of the pressure booster cylinder 5 with sufficient reaction times, all resulting from the different rolling forces roll gap changes. For this purpose, measured values required with the sensors 26 can be detected and supplied to the control unit 25.
  • 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 limitation also for forging presses or upsetting frames.

Landscapes

  • 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)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Pens And Brushes (AREA)
  • Color Printing (AREA)
  • Control Of Fluid Pressure (AREA)
  • Lubricants (AREA)

Abstract

For many applications pressure-medium cylinders have to achieve high adjusting forces which often impairs the dynamics of such cylinders due to the large piston cross sections and cylinder volumes, and/or pressure medium has to be supplied at very high pressure. The present invention shows a pressure-medium cylinder which has short reaction times, high adjusting forces and small overall sizes, which is achieved in that two cylinders 5, 8 are arranged in the pressure-medium cylinder 1, which cylinders can be activated independently of one another.

Description

Die gegenständliche Erfindung betrifft einen Druckmittelzylinder mit Druckübersetzung gemäß den Oberbegriff des Anspruchs 1, und eine Verwendung eines solchen Druckmittelzylinders als Anstellzylinder in einem Walzgerüst.The subject invention relates to a pressure cylinder with pressure transmission according to the preamble of claim 1, and a use of such a pressure cylinder as a positioning cylinder in a rolling stand.

Druckmittelzylinder müssen für bestimmte Anwendungen, z.B. in Walzgerüsten, hohe Kräfte aufbringen können und/oder genau positioneregelbar sein. Dazu kann ein Druckmittelzylinder, z.B. ein Hydraulikzylinder, mit einem Kolben mit großem Querschnitt vorgesehen werden und/oder der Druckmittelzylinder muss mit unter hohem Druck stehende Druckmittel versorgt werden. Im ersten Fall wird der Druckmittelzylinder sehr groß und im zweiten Fall muss für das Druckmittelsystem ein hoher Aufwand betrieben werden. Darüber hinaus muss bei großen Zylindern eine große Menge von Druckmittel bewegt werden, wodurch die Dynamik solcher Zylinder, also die Zeit um Stellbewegungen des Zylinders 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 arbeitet 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 Druckübersetzer, der einen Niederdruckzylinder und einen Arbeitszylinder in einem Gehäuse vereinigt. Bei einem solchen Druckübersetzer können die beiden Kolben jedoch nicht unabhängig voneinander angesteuert werden. Ansteuerbar ist lediglich der Niederdruckzylinder, der die Bewegung an einen Arbeitskolben überträgt. Damit ist aber auch der Bewegungsspielraum des Arbeitszylinders eingeschränkt, oder man benötigt wieder große Volumina und Abmessungen, wodurch wiederum die Dynamik leiden würde. Außerdem wird das Druckmittel für den Arbeitszylinder nicht von außen zugeführt, sondern ist im Druckübersetzer eingeschlossen, was zu Problemen mit Leckageverlusten führen kann und das Druckmittel regelmäßig nachgefüllt werden muss.Pressure cylinder must be able to apply high forces for certain applications, eg 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 large cylinders, a large amount of pressure medium must be moved, whereby the dynamics of such cylinders, so the time to perform actuator movements of the cylinder suffers.
From the DE 36 30 725 A Now, for example, a pressure increase is apparent to increase the pressure in the hydraulic supply line to a hydraulic cylinder. However, the pressure booster works here pneumatically, which makes two different supply media and the associated equipment necessary The problems described above can not be solved with such pressure intensifiers.
The WO 02/053920 A2 shows a hydraulic or hydropneumatic pressure booster, which unites 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 each other. Can be controlled only the low pressure cylinder, which transmits the movement to a working piston. But this also limits the range of motion of the working cylinder, or you again need large volumes and dimensions, which in turn would suffer the dynamics. In addition, the pressure medium for the working cylinder is not supplied from the outside, but is included in the pressure booster, which can lead to problems with leakage losses and the pressure medium must be replenished regularly.

Aus der US 2002/0029569 A1 ist ein hydraulischer Arbeitszylinder, gemäß den Oberbegriff des Anspruchs 1, zu entnehmen, in dem ein hydraulisch angesteuerter Druckverstärkerkolben den hydraulischen Druck auf den Arbeitszylinder erhöht. Zusätzlich is ein Wegmeßsystem zur Steuerung der Kolbenpositionen beschrieben. Dabei kann aber nur ein Kolben hinsichtlich seiner Position erfasst werden.From the US 2002/0029569 A1 is a hydraulic cylinder, according to the preamble of claim 1, refer to, in which a hydraulically driven pressure booster piston increases the hydraulic pressure on the working cylinder. In addition, a displacement measuring system for controlling the piston positions is described. However, only one piston can be detected with respect to its position.

US 5,207,267 offenbart einen Zylinder, die zwei miteinander In Wirkverbindung stehenden Kolben aufweist. Jede Kolbenstange weist eine eigene Messeeinrichtung auf, sodass eine aufwändigere Messvorrichtung nötig ist. US 5,207,267 discloses a cylinder having two pistons operatively connected to each other. Each piston rod has its own measuring device, so that a more complex measuring device is necessary.

Es ist daher eine Aufgabe der vorliegenden Erfindung einen Hydraulikzylinder anzugeben, der kompakt aufgebaut ist, hohe Anstellkräfte erzeugt und eine hohe Dynamik aufweist.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 einen Druckmittelzylinder mit Druckübersetzung gemäß Anspruch 1 gelöst.This object is achieved by a pressure medium cylinder with pressure transmission according to claim 1.

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 Zylinder kann zur Feinpositionierung unter hohem Druck und hoher Dynamik verwendet werden. Diese Maßnahmen erlauben somit eine wesentliche Reduktion der Zylinderbaugröße, ermöglicht einen Druckmittelzylinder auch als Langhubausführung auszuführen, z.B. für die Integration in einen Walzenständer, und bringt wesentliche Gewichts- und Fertigungskosteneinsparungen mit sich.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. coarsely prepositioned and the second cylinder can be used for fine positioning under high pressure and high dynamics. These measures thus allow a substantial reduction of the cylinder size, allows a pressure medium cylinder to perform as Langhubausführung, e.g. for integration into a roll stand, and involves significant weight and manufacturing 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 ausgestattet, mit dem die Position zumindest eines der beiden Zylinderkolbens erfasst werden kann, da die so erfassbare Istposition eines Kolben direkt für eine Regelung oder Steuerung 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 piston can be detected, since the thus detectable actual position of a piston can be used directly for a control or control.

Die vorliegende Erfindung wird im Nachfolgenden anhand der beispielhaften, schematischen und nicht einschränkenden Figuren 1 und 2 beschrieben. Dabei zeigt

  • Fig. 1 einen Schnitt durch einen erfindungsgemäßen Druckmittelzylinder und
  • Fig. 2 eine schematische Darstellung eines Walzgerüsts mit einem erfindungsgemäßen Druckmittelzylinder.
The present invention will now be described by way of example, schematic and not limitation FIGS. 1 and 2 described. It shows
  • Fig. 1 a section through a pressure cylinder according to the invention and
  • Fig. 2 a schematic representation of a roll 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, angeordnet sind. In den beiden Zylindern 5, 8 ist jeweils ein Kolben, ein Druckübersetzungskolben 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.
Der Druckübersetzungszylinder 5 und der Anstellzylinder 8 sind dabei hydraulisch voneinander getrennt und können über jeweils eine eigene Zuleitung 9, 11 und eigene Ableitung 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 verwendet werden kann oder mit einem solchen in Verbindung stehen kann. Der Anstellkolben 6 kann auch eine Vertiefung 15 in der Größe des Querschnitts der Drückübersetzungskolbenstange 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.
Der Druckübersetzungskolben 3 ist mit einer Druckübersetzungskolbenstange 4 verbunden, die in einer von einem Teil des Gehäuses 2 gebildeten Trennwand zwischen Druckübersetzungszylinder 5 und Anstellzylinder 8 geführt und durch diese hindurchgeführt ist und somit wirkungsmäßig mit dem Anstellzylinder 8 bzw. mit dem Hydraulikflüssigkeitsvolumen des Anstellzylinders 8 in Verbindung steht. Der Druckübersetzungskolben 3 und die Druckübersetzungskolbenstange 4 ist hier so dimensioniert, dass die Druckübersetzungskolbenstange 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 medium cylinder, here a hydraulic cylinder 1, after Fig. 1 has a housing 2 in which two cylinders, a pressure booster cylinder 5 and a setting cylinder 8, are arranged. In each of the two cylinders 5, 8, a piston, a pressure booster piston 3 and an adjusting piston 6 are arranged. 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.
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 own discharge 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 can be used for example as any actuator or can be associated with such. The Anstellkolben 6 may also have a recess 15 in the size of the cross section of the pressure transmission piston rod 4, as in Fig. 1 indicated to avoid contact, for example in case of malfunction, between the pressure transmission piston rod 4 and Anstellkolben 6 and a possible damage to the same.
The pressure booster piston 3 is connected to a pressure booster piston rod 4, which is guided in a partition wall formed by a part of the housing 2 between the pressure booster cylinder 5 and adjusting cylinder 8 and through this and thus operatively connected to the adjusting cylinder 8 and with the hydraulic fluid volume of the Anstellzylinders 8 in connection stands. The pressure booster piston 3 and the pressure booster piston rod 4 is dimensioned here such that the pressure booster piston rod 4 does not dive into the Anstellzylinderraum in an uppermost 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 Wegmesssystem 14, z.B. ein hinlänglich bekanntes elektrisches oder optisches System, verbunden ist. Das Wegmesssystem 14 kann z.B. mit einer Regelung des Hydraulikzylinders 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 translation piston rod 4, the pressure booster piston 3 and the housing of the hydraulic cylinder 1 and carried out with a suitable Wegmesssystem 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 operated 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.
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 können 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 bekannt mittels in der Zu- 9, 11 und/oder Ableitung 10, 12 angeordneten bekannten Servoventilen erfolgen.
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 übertragen. Das Wegmesssystem 14 kann mit einer geeigneten Regelung verknüpft sein. Der Druckübersetzerkolben 3 befindet sich zum Zeitpunkt der Positionierung des Anstellkolbens 6 in seiner obersten Lage und ist nicht aktiv. Nach der Positionierung des Anstellkolbens 6 und damit der Anstellkolbenstange 7 durch die Ansteuerung des Anstellzylinders 8 wird dessen Hydraulikzuleitung 11 z.B. mittels eines sperrbaren Ventils vom Hydrauliksystem getrennt und die Regelfunktion des Hydraulikzylinders 1 wird nun vom Druckübersetzerzylinder 5 über dessen Servoventil übernommen.
Durch die erfindungsgemäße Anordnung von Druckübersetzungskolben 3 und Anstellkolben 6 taucht nun die Druckübersetzungskolbenstange 4, deren Durchmesser in einem bestimmten Verhältnis zum Druckübersetzungskolbendurchmesser steht, in den Zylinderraum 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 Druckübersetzungszylinders 5 der Anstellkolben 6 mit einem multiplizierten Druck angesteuert und bewegt werden. Es ist mit dem erfindungsgemäßen Hydraulikzylinder 1 also möglich mit einem Hydrauliksystem relativ geringen Druckes und geringer Dimensionen den Anstellkolben 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 ergeben.The function of the hydraulic cylinder 1 according to the invention will be described below by way of example.
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 control of the cylinders 5, 8 can be done as well known by means arranged in the supply 9, 11 and / or discharge 10, 12 known servo valves.
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, to the displacement measuring system 14. The displacement measuring system 14 may be linked to a suitable control. The pressure booster piston 3 is located at the time of positioning of the Anstellkolbens 6 in its uppermost position and is not active. After the positioning of the Anstellkolbens 6 and thus the Anstellkolbenstange 7 by the control of the Anstellzylinders 8 whose hydraulic supply line 11 is separated for example by means of a lockable valve from the hydraulic system and the control function of the hydraulic cylinder 1 is now taken over by the pressure intensifier cylinder 5 via the servo valve.
The inventive arrangement of pressure booster piston 3 and Anstellkolben 6 now immersed the pressure booster piston rod 4, whose diameter is in a certain ratio to the pressure translation piston diameter, in the cylinder chamber of Anstellkolbens 6, which has the consequence that there multiplied by the ratio of pressure booster piston cross section to Druckübersetzungskolbenstangenquerschnitt Hydraulic pressure builds up. The control path of the intensifier multiplies by the same ratio. Thus, by controlling the pressure transmission cylinder 5 of the Anstellkolben 6 can be driven and moved with a multiplied pressure. 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 pressurize the Anstellkolben 6 with a x times the pressure of the hydraulic system.
In this example, the transmission ratio is about 1 to 4, ie 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.Such a hydraulic cylinder 1 can be used particularly advantageously as a setting cylinder 28 in a roll stand, as in Fig. 2 shown schematically.
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.

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. Ebenso 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 resultierenden 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 Druckübersetzungskolben 3 sofort wieder in die oberste Lage gefahren und die Regelung wieder an den Anstellzylinder 8 des Hydraulikzylinders 1 übergeben. Mit dessen erneuter Positionierung beginnt der nächste Zyklus.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 data from other sensors 26 as in Fig. 2 indicated. Likewise, the control unit 25 may 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 according to the specifications and under control of the pressure booster cylinder 5 with sufficient reaction times, all resulting from the different rolling forces 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 threading out of the rolled strip 23 from the roll stand 20, the pressure booster piston 3 is immediately returned to the topmost position and the control is again transferred to the setting cylinder 8 of the hydraulic cylinder 1. With its repositioning, the next cycle begins.

Es wäre aber selbstverständlich auch denkbar, beide Zylinder 5, 8 gleichzeitig anzusteuern, 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 Einschränkung 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 limitation also for forging presses or upsetting frames.

Ein erfindungsgemäßer Druckmittelzylinder wird oben am Beispiel eines Hydraulikzylinders 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.An inventive pressure medium cylinder 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 (9)

  1. Pressure-medium cylinder with pressure intensification, preferably the hydraulic or pneumatic cylinder, the pressure-medium cylinder (1) having arranged in it two cylinders (5, 8) which are separate from one another and in each of which a piston (3, 6) is arranged, and the piston (3) of the first cylinder (5) having a piston rod (4) which is operatively connected to the second cylinder (8) for the increase in pressure, the cylinders (5, 8) being able to be activated independently of one another, and the pressure-medium cylinder (1) having arranged on it a path measurement system (14), by means of which the movement of at least one of the two pistons (3, 6), preferably of the second piston (6), can be measured, characterized in that a measurement transmitter rod assembly (13) is provided, which is led through the first piston (3) and the first piston rod (4) and which is connected at one end to the second piston (6) or to its piston rod (7) and at the other end to the path measurement system (14).
  2. Pressure-medium cylinder according to Claim 1, characterized in that each cylinder (5, 8) has a specific supply line (9, 11) for pressure medium and a specific discharge line (10, 12) for pressure medium.
  3. Pressure-medium cylinder according to either one of Claims 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. Pressure-medium cylinder according to Claim 3, characterized in that the piston rod (4) of the first piston (3) is arranged so as to be guided in the housing (2) of the pressure-medium cylinder (1).
  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 pressure-medium cylinder (1).
  6. Use of the pressure-medium cylinder according to one of Claims 1 to 5 as an adjusting cylinder (28) of a roll (21) of a roll stand (20).
  7. Use according to Claim 6, characterized in that the second piston rod (7) is operatively connected to a roll (21) or a mounting of a roll (21) of a roll stand (20).
  8. Use of the pressure-medium cylinder according to one of Claims 1 to 7 as an adjusting cylinder (28) of a roll (21) of a roll stand (20).
  9. Use according to Claim 8, characterized in that the second piston rod (7) is operatively connected to a roll (21) or a mounting of a roll (21) of a roll stand (20).
EP05769977A 2004-07-02 2005-06-16 Pressure-medium cylinder with pressure-translation Expired - Lifetime EP1763638B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT0112304A AT500476B8 (en) 2004-07-02 2004-07-02 PRESSURE TRANSMISSION PRESSURE CYLINDER
PCT/EP2005/006476 WO2006002772A1 (en) 2004-07-02 2005-06-16 Pressure-medium cylinder with pressure-translation

Publications (2)

Publication Number Publication Date
EP1763638A1 EP1763638A1 (en) 2007-03-21
EP1763638B1 true EP1763638B1 (en) 2008-05-07

Family

ID=35045434

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05769977A Expired - Lifetime EP1763638B1 (en) 2004-07-02 2005-06-16 Pressure-medium cylinder with pressure-translation

Country Status (12)

Country Link
US (1) US7698893B2 (en)
EP (1) EP1763638B1 (en)
JP (1) JP4668991B2 (en)
CN (1) CN100532865C (en)
AT (2) AT500476B8 (en)
BR (1) BRPI0512936A (en)
CA (1) CA2572486C (en)
DE (1) DE502005004029D1 (en)
RU (1) RU2377446C2 (en)
SA (1) SA05260195B1 (en)
UA (1) UA84088C2 (en)
WO (1) WO2006002772A1 (en)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102392842A (en) * 2011-10-27 2012-03-28 中联重科股份有限公司 Crusher, hydraulic control system and hydraulic cylinder
DE102012008902A1 (en) 2012-05-08 2013-11-14 Tox Pressotechnik Gmbh & Co. Kg Hydropneumatic device for pressure transmission and riveting device
CN107002713B (en) * 2014-11-21 2019-11-12 Des公司 Fluid Flow Multiplier
CN104595275B (en) * 2014-11-30 2017-02-22 贵州红林机械有限公司 Three-position precise air cylinder
CN104525581A (en) * 2014-12-31 2015-04-22 太原磬泓机电设备有限公司 Roller spacing online dynamic adjustment device
EP3150292A1 (en) * 2015-10-02 2017-04-05 Primetals Technologies Austria GmbH Positioning device
US10138729B2 (en) * 2016-10-20 2018-11-27 Deere & Company Drive assembly with pressure force aggregating piston arrangement for hydraulic motor speed/torque selector
WO2018190756A1 (en) * 2017-04-11 2018-10-18 Saab Ab A fluid actuator arrangement and a method for control of a fluid actuator arrangement
CN111729614A (en) * 2020-07-06 2020-10-02 郑州康拜特超硬材料有限公司 Cubic apparatus press and manufacturing method thereof

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE613343C (en) * 1935-05-17 Reineke Regler Vertriebsgesell Multi-pass mill for rolling several strands at the same time
DE1253660B (en) * 1962-02-15 1967-11-09 Neumann O H G Rolling frame with closed stands and a control device for tolerance-compliant rolling
CA923790A (en) * 1970-10-30 1973-04-03 J. Beneteau Donald Pressure intensifier cylinder
US3883938A (en) * 1974-03-04 1975-05-20 Alfred W Schmidt Fluid-powered crimping press
US4481800A (en) * 1982-10-22 1984-11-13 Kennecott Corporation Cold rolling mill for metal strip
SU1298429A1 (en) * 1984-09-13 1987-03-23 И. Е. Малкиман, Б. Е. Рузинов и Л. М. За рузный Hydropneumatic cylinder
GB8513553D0 (en) * 1985-05-29 1985-07-03 Davy Mckee Poole Hydraulic ram assembly
SU1740803A1 (en) * 1990-05-24 1992-06-15 Машиностроительный Завод "Звезда" Pneumatic and hydraulic amplifier
US5207267A (en) * 1990-08-09 1993-05-04 Toshiba Kikai Kabushiki Kaisha Injection control method of die cast machine
EP0618021B1 (en) * 1993-03-29 1996-01-03 Siemens Aktiengesellschaft Method and device for hydraulic roll-gap control
DE4445011A1 (en) * 1994-12-16 1996-06-20 Tox Pressotechnik Gmbh Hydraulic pressure intensifier
JP2000009104A (en) * 1998-06-19 2000-01-11 Akio Wada Hydraulic mechanism
JP3034862B1 (en) * 1999-02-23 2000-04-17 三菱電機株式会社 Seam welding machine
JP3598235B2 (en) * 1999-03-10 2004-12-08 Ｓｍｃ株式会社 Pressure flow control valve
JP4402264B2 (en) * 1999-08-11 2010-01-20 三菱重工業株式会社 Rolling mill
JP3417475B2 (en) * 2000-03-02 2003-06-16 マイクロハード株式会社 Cylinder device for rolling mill hydraulic pressure reduction
JP2004503702A (en) * 2000-03-27 2004-02-05 トックス・プレッソテヒニック・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング・ウント・コンパニー・コマンディトゲゼルシャフト Hydraulic intensifier
US6591736B2 (en) * 2000-08-30 2003-07-15 Aisin Seiki Kabushiki Kaisha Master cylinder
JP3474840B2 (en) * 2000-09-11 2003-12-08 株式会社南武 Hydraulic cylinder pressure booster
JP3364215B1 (en) * 2002-03-12 2003-01-08 有限会社本田製作所 Double-acting booster cylinder and method of boosting pressure in cylinder

Also Published As

Publication number Publication date
EP1763638A1 (en) 2007-03-21
JP4668991B2 (en) 2011-04-13
AT500476B1 (en) 2006-07-15
CN1989349A (en) 2007-06-27
BRPI0512936A (en) 2008-04-15
US20070289440A1 (en) 2007-12-20
AT500476A1 (en) 2006-01-15
CA2572486C (en) 2013-08-20
CN100532865C (en) 2009-08-26
DE502005004029D1 (en) 2008-06-19
AT500476B8 (en) 2007-02-15
UA84088C2 (en) 2008-09-10
RU2377446C2 (en) 2009-12-27
CA2572486A1 (en) 2006-01-12
WO2006002772A1 (en) 2006-01-12
JP2008504499A (en) 2008-02-14
US7698893B2 (en) 2010-04-20
RU2007104052A (en) 2008-08-10
ATE394599T1 (en) 2008-05-15
SA05260195B1 (en) 2008-03-29

Similar Documents

Publication Publication Date Title
DE60310487T2 (en) Pilot-operated seat valve arrangement with integrated pressure-compensating arrangement
DE102008007651B3 (en) Positioner for double acting pneumatic actuator, double acting pneumatic actuator and method for operating double acting pneumatic actuator
EP1664551B1 (en) Control system and method for supplying pressure means to at least two hydraulic consumers
EP3050745B1 (en) Pneumatic control and measuring apparatus and seat comfort system
DE102009017506A1 (en) Pressure compensated hydraulic control valve with load-dependent pressure limitation
EP2518331A1 (en) Valve device
DE102008014963A1 (en) Position control mechanism for single-acting pneumatic cylinders
EP1763638B1 (en) Pressure-medium cylinder with pressure-translation
DE2921464A1 (en) CONTROL SYSTEMS
DE2108783C3 (en) Device for the automatic control of the thickness of flat rolled material
EP2435715B1 (en) Digital hydraulic controller
DE1176443B (en) Arrangement for the automatic control of liquid gears according to the displacement principle
DE10225691A1 (en) Control device for proportionally adjustable hydraulic pump of closed hydraulic circuit includes valve configuration with valve for each swivel direction of piston and a mechanical touch
DE2848021B1 (en) Deflection adjustment roller
DE102004014293B4 (en) Adjustment unit
EP2329895B1 (en) Press brake and bending tool with holding device for a workpiece
DE102008032522A1 (en) Rolling device with adjusting device
EP0676547B1 (en) Flow control device for a high pressure hydraulic system and a valve for a load-lowering brake
EP3918207B1 (en) Controlling hydraulic actuating cylinders in roll stands
EP0382057B2 (en) Automatically load-dependant brake force control
EP2516737B1 (en) Assembly for controlling the position of a roll or the nip pressure of a roll nip of a fibrous material web machine
DE102021006222B3 (en) Press device and 2/2-way proportional poppet valve
DE102019204208A1 (en) Device for cooling water suction for a robot installation plate with adjustable suction volume
DE2616059C3 (en) Combined electro-pneumatic and purely pneumatic braking device, especially for rail vehicles
WO2011072772A1 (en) Load detection circuit

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20061222

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU MC NL PL PT RO SE SI SK TR

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SIEMENS VAI METALS TECHNOLOGIES GMBH & CO

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU MC NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REF Corresponds to:

Ref document number: 502005004029

Country of ref document: DE

Date of ref document: 20080619

Kind code of ref document: P

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080507

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080818

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080507

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080907

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080507

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080507

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080507

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080507

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080507

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081007

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20090210

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080507

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080807

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080616

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090630

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080507

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081108

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080808

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20120626

Year of fee payment: 8

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20130610

Year of fee payment: 9

Ref country code: SE

Payment date: 20130607

Year of fee payment: 9

Ref country code: LU

Payment date: 20130621

Year of fee payment: 9

Ref country code: CZ

Payment date: 20130610

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20130703

Year of fee payment: 9

Ref country code: FI

Payment date: 20130613

Year of fee payment: 9

Ref country code: TR

Payment date: 20130531

Year of fee payment: 9

Ref country code: NL

Payment date: 20130603

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 20130710

Year of fee payment: 9

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130616

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20140819

Year of fee payment: 10

REG Reference to a national code

Ref country code: NL

Ref legal event code: V1

Effective date: 20150101

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140616

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140617

Ref country code: CZ

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140616

Ref country code: FI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140616

REG Reference to a national code

Ref country code: SE

Ref legal event code: EUG

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20140616

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20150227

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150101

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140616

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140630

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502005004029

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160101

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140630

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140616