EP1763638A1 - Cylindre a agent sous pression avec conversion de pression - Google Patents

Cylindre a agent sous pression avec conversion de pression

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)
English (en)
Other versions
EP1763638B1 (fr
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/fr
Application granted granted Critical
Publication of EP1763638B1 publication Critical patent/EP1763638B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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.

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)
  • Color Printing (AREA)
  • Pens And Brushes (AREA)
  • Control Of Fluid Pressure (AREA)
  • Lubricants (AREA)

Abstract

Les cylindres à agent sous pression doivent être compatibles avec de nombreuses applications faisant intervenir des forces de réglage importantes, ce qui altère fréquemment la dynamique de ces cylindres, en raison de leurs sections et volumes importants, et/ou l'agent sous pression doit être fourni sous une pression très élevée. A cet effet, la présente invention a pour objet un cylindre à agent sous pression qui se caractérise par des temps de réaction limités, des forces de réglage importantes, et des encombrements réduits. Pour cela, deux cylindres (5, 8) sont disposés à l'intérieur du cylindre à agent sous pression (1) et peuvent être commandés indépendamment l'un de l'autre.
EP05769977A 2004-07-02 2005-06-16 Cylindre a agent sous pression avec conversion de pression Expired - Lifetime EP1763638B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT0112304A AT500476B8 (de) 2004-07-02 2004-07-02 Druckmittelzylinder mit druckübersetzung
PCT/EP2005/006476 WO2006002772A1 (fr) 2004-07-02 2005-06-16 Cylindre a agent sous pression avec conversion de pression

Publications (2)

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

Family

ID=35045434

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05769977A Expired - Lifetime EP1763638B1 (fr) 2004-07-02 2005-06-16 Cylindre a agent sous pression avec conversion de pression

Country Status (12)

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

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102392842A (zh) * 2011-10-27 2012-03-28 中联重科股份有限公司 破碎机及液压控制系统、液压缸
DE102012008902A1 (de) * 2012-05-08 2013-11-14 Tox Pressotechnik Gmbh & Co. Kg Hydropneumatische Vorrichtung zur Druckübersetzung und Nietvorrichtung
EP3221593A1 (fr) * 2014-11-21 2017-09-27 Des S.r.l. Multiplicateur de débit d'écoulement de fluide
CN104595275B (zh) * 2014-11-30 2017-02-22 贵州红林机械有限公司 一种三位置精密气缸
CN104525581A (zh) * 2014-12-31 2015-04-22 太原磬泓机电设备有限公司 一种轧辊辊距在线动态调整装置
EP3150292A1 (fr) * 2015-10-02 2017-04-05 Primetals Technologies Austria GmbH Dispositif de mise en contact
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 (fr) * 2017-04-11 2018-10-18 Saab Ab Agencement d'actionneur à fluide et procédé de commande d'un agencement d'actionneur à fluide
CN111729614A (zh) * 2020-07-06 2020-10-02 郑州康拜特超硬材料有限公司 一种六面顶压机及其制造方法

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EP0618021B1 (fr) * 1993-03-29 1996-01-03 Siemens Aktiengesellschaft Procédé et dispositif pour régler hydrauliquement l'emprise de laminage
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Also Published As

Publication number Publication date
WO2006002772A1 (fr) 2006-01-12
RU2007104052A (ru) 2008-08-10
AT500476B8 (de) 2007-02-15
DE502005004029D1 (de) 2008-06-19
US7698893B2 (en) 2010-04-20
CA2572486C (fr) 2013-08-20
RU2377446C2 (ru) 2009-12-27
SA05260195B1 (ar) 2008-03-29
JP2008504499A (ja) 2008-02-14
EP1763638B1 (fr) 2008-05-07
CA2572486A1 (fr) 2006-01-12
UA84088C2 (ru) 2008-09-10
CN100532865C (zh) 2009-08-26
BRPI0512936A (pt) 2008-04-15
ATE394599T1 (de) 2008-05-15
JP4668991B2 (ja) 2011-04-13
CN1989349A (zh) 2007-06-27
AT500476B1 (de) 2006-07-15
AT500476A1 (de) 2006-01-15
US20070289440A1 (en) 2007-12-20

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