EP0242783A2 - Cage pour laminage ou calandrage - Google Patents

Cage pour laminage ou calandrage Download PDF

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Publication number
EP0242783A2
EP0242783A2 EP87105563A EP87105563A EP0242783A2 EP 0242783 A2 EP0242783 A2 EP 0242783A2 EP 87105563 A EP87105563 A EP 87105563A EP 87105563 A EP87105563 A EP 87105563A EP 0242783 A2 EP0242783 A2 EP 0242783A2
Authority
EP
European Patent Office
Prior art keywords
roll
bearing
bearings
roller
force
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
EP87105563A
Other languages
German (de)
English (en)
Other versions
EP0242783A3 (en
EP0242783B1 (fr
Inventor
Günther Alich
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.)
Individual
Original Assignee
Individual
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
Priority claimed from CH161686A external-priority patent/CH669917A5/de
Priority claimed from CH2654/86A external-priority patent/CH670777A5/de
Application filed by Individual filed Critical Individual
Publication of EP0242783A2 publication Critical patent/EP0242783A2/fr
Publication of EP0242783A3 publication Critical patent/EP0242783A3/de
Application granted granted Critical
Publication of EP0242783B1 publication Critical patent/EP0242783B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • D—TEXTILES; PAPER
    • D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21G—CALENDERS; ACCESSORIES FOR PAPER-MAKING MACHINES
    • D21G1/00—Calenders; Smoothing apparatus
    • D21G1/02—Rolls; Their bearings
    • D21G1/0206—Controlled deflection rolls
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B29/00—Counter-pressure devices acting on rolls to inhibit deflection of same under load, e.g. backing rolls ; Roll bending devices, e.g. hydraulic actuators acting on roll shaft ends
    • D—TEXTILES; PAPER
    • D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21G—CALENDERS; ACCESSORIES FOR PAPER-MAKING MACHINES
    • D21G1/00—Calenders; Smoothing apparatus
    • D21G1/002—Opening or closing mechanisms; Regulating the pressure

Definitions

  • the invention relates to a roll stand with a fixedly mounted and at least one deliverable roll, the double-sided bearing journals of the latter each being guided in a bearing arrangement which can be displaced relative to the fixedly mounted roll by means of an adjusting mechanism for the purpose of adjusting the roll gap.
  • the invention has for its object to design a roll stand so that a high accuracy in maintaining the roll gap can be achieved without extreme demands on the storage, in particular of the roll that can be delivered, and also in applications where the reaction forces of the rolling stock on the pair of rolls are low or are indefinite.
  • the claim 2 calls an advantageous combination of actuator and force element.
  • the one roller 2 is fixedly mounted in the roller stand 1, while the other roller 4 can be moved relative to the roller 2 in order to change the roller gap 5 through which the material web 6 (FIG. 2) passes.
  • the double-sided bearing journals 8A and 8B of the roller 4 are each guided in a bearing arrangement 10A, 10B, and each of these bearing arrangements can be displaced essentially radially relative to the roller 2 by means of an associated adjusting mechanism described in more detail below.
  • the roller drive is not shown for the sake of simplicity. It can be a roll stand for the finish rolling of plastic or metal foils etc. or, for example, a calender with coating rolls for finishing, in particular coating material webs, i.e. preferably for applications in which it is necessary to maintain a relatively narrow roll gap 5 with high absolute Accuracy (in the range of micrometers) and with little or practically no counterforces (deformation forces) on the part of the material web on the rollers.
  • the bearing arrangement 10A, 10B associated with each bearing journal 8A, 8B of the deliverable roller 4 has two separate radial bearings 11 and 12 mounted next to one another (these, as well as the system parts described below, are only shown on the left in FIG. 1 because both sides are constructed identically). At least one of these bearings on each side of the roller is accommodated in a bearing plate connected to the roller stand (indicated schematically at 17 in FIG. 2) so as to be displaceable in the infeed direction, but the radial deflection of the roller 4 can also be prevented by other means.
  • One of the two radial bearings for example the bearing 11 closer to the roll barrel, is connected to a hydraulic actuating cylinder 13 (cylinder / piston unit) serving as a guided actuating member, while the other bearing 12 is connected to a force member 14, which is likewise designed here as a hydraulic actuating cylinder which exerts a force on the bearing 12 which is opposite to the (positive) feed direction of the actuator 13.
  • the frictional connection during the roller feed is established by connecting the (bilateral) actuators and the force organs to the roller stand 1.
  • both members 13 and 14 exerts a constant tension on the bearing 12, but the force member could in principle also, as indicated by dash-dotted lines in FIG. 1 , to be arranged opposite the actuator 13 and load the bearing 12 with pressure.
  • 1 selected equilateral arrangement of both organs 13 and 14 and design of the force element as a tie rod has the advantage that temperature-related dimensional changes in the stand on the one hand and in the rollers and the adjusting mechanism on the other hand practically cancel each other out and thus have no influence on the width of the nip 5 stay.
  • the hydraulic actuating cylinder 13 is connected to the pressure source 30 (hydraulic pump unit) via a hydraulic control valve 31 and the lines 32 and 36; the actuating cylinders 14 are also connected to the same pressure source via a pressure control valve 33 and lines 34.
  • a control amplifier 24 for each side is supplied on the one hand with a measurement signal generated by a roller spacer 20 as the actual value via line 21 and on the other hand with an adjustable setpoint signal via line 22.
  • the output signal generated by the control amplifier 24 is sent as a control value via the line 25 to the control valve 31.
  • FIG. 3 differs from the one described above essentially only in the design of the actuating member and the power member, which is why only the mounting of one side of the deliverable roller 4 is shown and the fixed roller 2 is only indicated; Parts of the plant which correspond to those according to FIGS. 1 and 2 are identified by the same reference numerals as there.
  • a double-acting hydraulic actuator cylinder 13 ⁇ provided, which is connected via lines 32 and 32 ⁇ to a corresponding electro-hydraulic control valve 31 ⁇ .
  • a pressure limiting valve 37 is preferably connected to the pressure line 32 for the positive feed direction of the roller 4, for reasons which are explained below in connection with the mode of operation.
  • a mechanical tie rod (expansion anchor) 15 is connected to the second bearing 12 as a force element.
  • this consists, for example, of two parts screwed into one another, one of which is rotatably anchored to the bearing 12 and the other to the roller stand 1; a lock nut 16 is indicated as a simple possibility for fixing the length during operation.
  • this simple embodiment of a length-adjustable tie rod is chosen only to illustrate the principle of operation of the arrangement;
  • a low-friction, torque-free ball screw with a remote-controlled, motorized rotary drive is known for a comfortable and precise length adjustment, a design known per se, whereby a gear with self-locking is to be used for the exact fixing of the adjustable anchor length.
  • the mechanical tie rod 15 is to be dimensioned and the basic setting of its length is to be selected such that it is already pretensioned by the actuator 13 'at the largest gap opening 5 to be set between the rollers 2, 4 and over the operational setting range of the gap width (working range of the Regulation or the actuating cylinder 13 ⁇ ) is claimed in the elastic expansion range, so in the "closing direction", ie with a decreasing gap width, the pulling force of the armature 15 counteracting the actuating force of the cylinder 13 ⁇ increases.
  • the prestressed, mechanical anchor 15 thus permanently eliminates play in the bearing arrangement 10 and in cooperation with the actuator 13 ⁇ a perfect, positive and non-positive guidance of the bearing pin 8 in the adjustment range.
  • the characteristic curve 38 shows the course of the counterforce exerted by the force element as a function of the gap width s of the roller gap 5, for example the “spring characteristic curve” according to Hooke's law of an elastically stretched tie rod.
  • the operational range of the actuator when regulating the gap width s is denoted by H; the respective position in operation changes within this range on the one hand as a result of setpoint changes, but also as a result of interferences such as eccentricity or out-of-roundness of the rolls during the roll rotation.
  • F b the maximum possible actuating force of the actuating member
  • the roll journals 8 and 8 zust of the deliverable roll 4 or the fixedly mounted roll 2 are each held in two separate radial bearings 11, 12 and 11 ⁇ , 12 ⁇ .
  • the roller 2 is fixedly mounted with respect to the stand 1.
  • the roller 4 can be fed to the roller 2 for the purpose of adjusting the gap width 5 and is not connected to the stand 1, it is only guided laterally to prevent pendulum movements (for example by means of guides fastened to the stand on both sides of the bearing 11, not shown).
  • a hydraulic actuating cylinder 13 is used as the actuator, the cylinder of which is attached to the bearing 11 'and the piston rod of which is attached to the bearing 11. Contrary to the feed direction of the actuating cylinder 13, the other pair of bearings 12, 12, is braced by means of four compression springs 45, as a result of which any bearing play is permanently eliminated.
  • the springs 45 are through Two parallel guide rods 44 are positioned, which extend between the arms of the bearings 12, 12 und and slide in the same guide holes.
  • a carrier 40 is also slidably guided on the guide rods 44 and held approximately in the middle between the rollers 2 and 4 between two compression springs 45.
  • non-contact measuring elements 43 of known construction, each of which provides an electrical signal for the distance to the bale surface ; a signal for the distance of the rolls or the width of the roll gap 5 can be formed from the individual signals in a manner known per se, see e.g. U.S. Patent No. 3,902,114 by the same applicant.
  • a control circuit for the automatic control of the gap width is indicated only schematically and in a simplified manner with actual value line 21, control amplifier 24, setpoint input 22, control signal line 25, control valve 31, hydraulic pump 30 and hydraulic pressure line 32 to the control cylinder 13.
  • Each of these bearings 52, 52 ⁇ is designed as a sliding shoe, formed from two supporting bodies 54 and 54 ⁇ , which are rigidly connected in pairs by a shield 53, 53 ⁇ . Between the bearings 11 and 11 ⁇ , in turn, two parallel guide rods 56 extend, on which each bearing shoe 52, 52 ⁇ is slidably guided by means of holes provided in the support bodies. Compression springs 55 are provided as the force organs counteracting the actuator 13 and are guided between the bearings 52, 52 'in the bores of the support body.
  • the support bodies 54, 54 ⁇ are preferably provided with wear-resistant bearing surfaces, on which the spring forces are slidably transmitted to the rollers and from their pins back to the bearings 11, 11 ⁇ .
  • the compression springs 55 it is also possible, for example, to use one or more hydraulic pressure cylinders (with constant counterforce) or, if appropriate, massive, adjustable compression rods as particularly "hard” mechanical springs.
  • the support bodies 54, 54 ⁇ can be provided with roller bearings instead of the sliding pads.
  • electromotive actuating spindle drives can also be used as actuators in the sense of the invention for slow-speed rollers.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Paper (AREA)
  • Casting Or Compression Moulding Of Plastics Or The Like (AREA)
EP19870105563 1986-04-22 1987-04-14 Cage pour laminage ou calandrage Expired - Lifetime EP0242783B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CH161686A CH669917A5 (en) 1986-04-22 1986-04-22 Double-acting bearings for roll pins
CH1616/86 1986-04-22
CH2654/86A CH670777A5 (fr) 1986-07-02 1986-07-02
CH2654/86 1986-07-02

Publications (3)

Publication Number Publication Date
EP0242783A2 true EP0242783A2 (fr) 1987-10-28
EP0242783A3 EP0242783A3 (en) 1988-02-10
EP0242783B1 EP0242783B1 (fr) 1990-10-03

Family

ID=25688169

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19870105563 Expired - Lifetime EP0242783B1 (fr) 1986-04-22 1987-04-14 Cage pour laminage ou calandrage

Country Status (2)

Country Link
EP (1) EP0242783B1 (fr)
DE (1) DE3765289D1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0351507A3 (en) * 1988-07-16 1990-12-27 Gunther Alich Device for adjusting the interstice between rollers
WO2001023667A1 (fr) * 1999-09-24 2001-04-05 Metso Paper, Inc. Calandre
DE10125378A1 (de) * 2001-05-23 2002-11-28 Voith Paper Patent Gmbh Verfahren zur Einstellung der Anpressung zweier aneinander annäherbarer achsparalleler Walzen sowie Anordnung zum gegenseitigen Andrücken solcher Walzen
US7018475B2 (en) 2001-05-23 2006-03-28 Voith Paper Patent Gmbh Device, method and arrangement for pressing two axis-parallel rollers approachable to one another in a device for producing and/or treating a web of material
DE102008012072B3 (de) * 2008-02-29 2009-08-13 Windmöller & Hölscher Kg Eine Vorrichtung und ein Verfahren zum formatmäßigen Auftragen von Leim bzw. Klebstoff auf Werkstücke
CN110328230A (zh) * 2019-06-27 2019-10-15 西安泰力松新材料股份有限公司 一种焊带压延机
CN116078824A (zh) * 2022-12-07 2023-05-09 中国电子科技集团公司第四十六研究所 一种两辊压延机消游隙油缸系统

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB747347A (en) * 1952-12-23 1956-04-04 William Meikle Cochran Improvements relating to calenders and rolling mills
DE1150272B (de) * 1959-05-29 1963-06-12 Voith Gmbh J M Glaettwerk fuer Papierbahnen od. dgl.
DE1184621B (de) * 1962-11-03 1964-12-31 Jean Hiedemann Fa Druckgebungssystem fuer Walzenkalander, insbesondere zum Praegen von Papier, Pappe od. dgl.
GB1133944A (en) * 1965-03-24 1968-11-20 Kleinewefers Soehne J Device for compensating for the deflection of calender rolls
US3347157A (en) * 1965-04-30 1967-10-17 Farrel Corp Roll structures and method
US3448683A (en) * 1966-12-16 1969-06-10 Adamson United Co Calender with removable bearing pressure mechanism
US3902114A (en) * 1967-10-20 1975-08-26 Gunther Alich Method of and apparatus for measuring the distance between cooperating rollers of a rolling mill
DE1936769A1 (de) * 1969-07-19 1971-02-04 Demag Ag Vorrichtung zur Balligkeitssteuerung der Arbeitswalzen in einem Duo-Metallwalzwerk
DE2801558C2 (de) * 1978-01-14 1986-11-20 Basf Ag, 6700 Ludwigshafen Kalanderwalzenanordnung

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0351507A3 (en) * 1988-07-16 1990-12-27 Gunther Alich Device for adjusting the interstice between rollers
WO2001023667A1 (fr) * 1999-09-24 2001-04-05 Metso Paper, Inc. Calandre
US6848358B1 (en) 1999-09-24 2005-02-01 Metso Paper, Inc. Calender
DE10125378A1 (de) * 2001-05-23 2002-11-28 Voith Paper Patent Gmbh Verfahren zur Einstellung der Anpressung zweier aneinander annäherbarer achsparalleler Walzen sowie Anordnung zum gegenseitigen Andrücken solcher Walzen
US7018475B2 (en) 2001-05-23 2006-03-28 Voith Paper Patent Gmbh Device, method and arrangement for pressing two axis-parallel rollers approachable to one another in a device for producing and/or treating a web of material
US7445693B2 (en) 2001-05-23 2008-11-04 Voith Paper Patent Gmbh Device, method and arrangement for pressing two axis-parallel rollers approachable to one another in a device for producing and/or treating a web of material
DE102008012072B3 (de) * 2008-02-29 2009-08-13 Windmöller & Hölscher Kg Eine Vorrichtung und ein Verfahren zum formatmäßigen Auftragen von Leim bzw. Klebstoff auf Werkstücke
CN110328230A (zh) * 2019-06-27 2019-10-15 西安泰力松新材料股份有限公司 一种焊带压延机
CN116078824A (zh) * 2022-12-07 2023-05-09 中国电子科技集团公司第四十六研究所 一种两辊压延机消游隙油缸系统

Also Published As

Publication number Publication date
DE3765289D1 (de) 1990-11-08
EP0242783A3 (en) 1988-02-10
EP0242783B1 (fr) 1990-10-03

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