US3286495A - Deformation compensating hydraulic device for rolling mills of the hydraulic mechanical pressure type - Google Patents

Deformation compensating hydraulic device for rolling mills of the hydraulic mechanical pressure type Download PDF

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Publication number
US3286495A
US3286495A US343380A US34338064A US3286495A US 3286495 A US3286495 A US 3286495A US 343380 A US343380 A US 343380A US 34338064 A US34338064 A US 34338064A US 3286495 A US3286495 A US 3286495A
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United States
Prior art keywords
hydraulic
screwdown
circuit
pressure
roll
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Expired - Lifetime
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US343380A
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English (en)
Inventor
Diolot Lucien
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Societe Nouvelle Spidem
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Societe Nouvelle Spidem
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    • 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
    • B21B37/64—Mill spring or roll spring compensation systems, e.g. control of prestressed mill stands

Definitions

  • the distance between the chocks is initially set at each end of the roll stand by means of ram cylinders of the short stroke, large section type, each being connected through hydraulic conduits to a screwdown cylinder of the long stroke, small section type.
  • the pistons of the screwdown cylinders are driven by electric motors, the output of which, as it is well-known by those skilled in the art, may be substantially less than that of the motors used in non-hydraulic screwdown systems of equivalent efficiency.
  • the invention provides a hydraulic conduit communicating with the ram cylinder in each chock and an equalizing cylinder, electric means for sensing the pressure fluctuations in the ram cylinders due to roll deformations, and means for electrically actuating a valve mechanism in response to the electrically sensed pressure fluctuations, said valve being adapted to control the admission of servo pressure into a control cylinder to counteract the fluctuating pressures caused .by the roll deformation.
  • each stand 1, 1' supports a lower chock 2, 2' and an upper chock 3, 3, respectively. Between each of the lower chocks 2, 2' there is positioned a lower working roll 4, While between the upper chocks 3, 3' there extends an upper working roll 4'. With each lower chocks 2, 2' there is associated a conventional short stroke, large section type hydraulic ram cylinder 6, 6'.
  • the screwdown pressure in the two rarn cylinders 6, 6' is set by the screwdown cylinders 7, 7', the pistons of which, in turn, are advanced or retracted by electric screwdown motors 9, 9' linked to the pistons by means of a reduction gear assembly 8, 8', respectively.
  • the motors 9, 9' are interconnected by a clutch 10, generally of the magnetic type.
  • Screwdown cylinder 7 and ram cylinder 6 are connected through a hydraulic conduit 11, While screwdown cylinder 7' communicates with ram cylinder 6' by means of a hydraulic conduit 11.
  • Ram cylinders 6 and 6 further communicate through conduits 12, 12' with the right hand chamber of equalizing cylinders l3, 13', respectively.
  • both equalizing cylinders 13, 13' there is slid-ably disposed a piston the function of which will become apparent as the specification progresses.
  • the piston in both equalizing cylinders 13, 13' are, on one hand, mechanically interconnected and are, on the other hand, joined with the piston of a control cylinder 14.
  • the mechanical linkage between the pistons in cylinders 13, 13 and 14 may be etfectuated simply by arranging said cylinders along the same axis and joining the three pistons with a single rod 2% It is well understood that the spaced relation and the axial disposition of cylinders 13, 13' and 14 described hereinbefore and schematically illustrated in the drawing should by no means be construed as limiting the inventive system.
  • the three cylinders 13, 13' and 14 may be replaced by an equivalent unitary device having expansible chambers and mechanically interconnected pistons slidable therein.
  • control cylinder 14 is associated with a second hydraulic circuit independent of, and separated from the precedingly described screwdown circuit.
  • This second hydraulic circuit comprises a reservoir 18, a pressure accumulator 16 supplied with hydraulic liquid from reservoir 18 by means of a pump 17.
  • the second hydraulic circuit further comprises a solenoid valve 15 which controls the admission of hydraulic liquid into cylinder 14 in a manner as will be explained hereinafter.
  • At least one of the ram cylinders 6, 6' is connected to a pressure gauge 22 adapted to sense all pressure variations in the ram cylinders 6, 6' and, accordingly, emit an electric signal when such variations are sensed.
  • the electric signals emitted by gauge 22 are fed into a bridge circuit 2 3 of a controller 21.
  • Amplfier 24, associated with bridge 23, is adapted to emit an actuating signal for energizing solenoid valve 15.
  • the free end of rod 20, distal from cylinder 14, is attached to a potentiometer 25 which, in turn, is in circuit with bridge 23.
  • the desired clearance and parallelism between working rolls 4, 4 is set by means of energizing the screwdown motors 9, 9'.
  • the pressure in the screwdown circuit and in the cylinders 13, 13' is adapted to maintain the work roll 4 in balance in its desired position with respect to work roll 4'.
  • the pressure signal fed into bridge 23 from gauge 22 and the effect of the resistance of potentiometer 25, as set by the pre-operational position of rod 2 cancel each other and as a result, no actuating signal appears at the output of amplifier 24.
  • the increase of pressure in the clampdown circuit due to the separation of the work rolls has two immediate effects: (1) the electric signal fed from pressure gauge 22 into bridge '23 is increased; (2) the rod 20 is displaced in the direction of the arrow 19 due to the increase of pressure in the right hand chambers of actuating cylinders 13, 13'.
  • the displacement of rod 20 causes potentiometer 25 to change its previous, balanced value.
  • the comparison of the new signal from gauge 22 and the new value of potentiometer 25 results in a correcting output signal from bridge 23 through amplifier 24 energizing solenoid valve 15.
  • the valve 15 establis'hes communication between the left hand chamber of cylinder 14 and pressure accumulator 16 causing hydraulic liquid to be injected into control cylinder 14.
  • the new pressure in the left hand chamber of cylinder 14 is sufficiently large to overcome the pressure in the screw circuit and thus, in cylinders 13, 13'. As a consequence, rod 20 will now move towards its original position.
  • the return motion of rod 20 has two immediate effects: First, the volume of the right hand chambers gradually decreases causing the hydraulic liquid to be displaced therefrom. The increased pressure in the clampdown circuit results in an expansion of ram cylinders 6, 6' forcing roll 4 to assume its preset position. Secondly, the potentiometer is moved back by rod 20 towards its original setting.
  • the invention provides a rolling pressure compensating system that operates with the exclusion of the screwdown mechanism and having therefore a low inertia, is capable of instantaneous response and correction.
  • a system for compensating for the deformation of working rolls in rolling mills of the type including a screwdown mechanism associated with ram cylinders through a hydraulic screwdown circuit containing a constant volume of hydraulic fluid to adjust the roll supporting chocks to a roll clearance of predetermined value, comprising (a) expansible equalizing means communicating with said screwdown circuit and adapted to receive therefrom and release thereinto amounts of said fluid as the pressure in said circuit varies in response to the changes in said clearance caused by fluctuating roll separating forces,
  • said equalizing means includes (1) expansible equalizing chamber means communicating with said screwdown circuit and adapted to receive therefrom and release thereinto amounts of said fluid as the pressure in said circuit varies in response to changes of said clearance caused by fluctuating roll separating forces and (2) follower means mechanically connected to said expansible chamber means and adapted to be displaced by the change of volume of said expansible chamber means and cause a change of volume thereof when actuated by said hydraulic servo means, said follower means further adapted to generate, when being displaced, a changing signal in said circuit means.
  • said hydraulic servo system includes (1) expansible control chamber means operatively associated with said equalizing means to cause said last named means to expand or contract,
  • solenoid valve means adapted to admit to or drain hydraulic fluid from said control chamber means to cause expansion or contraction thereof, said solenoid valve means being energized by said electric circuit means.
  • gauge means communicating with said screwdown circuit and adapted to generate electric signals proportional to the pressure change in said ram cylinders.
  • equalizing means includes (1) at least one equalizing cylinder having a slideable piston therein,
  • said hydraulic servo means includes l) a control cylinder axially aligned with said equalizing cylinder and having a slideable piston therein,
  • solenoid valve means adapted to admit to or drain hydraulic liquid from said control cylinder, said piston rod being rigidly attached to said piston slideable in said control cylinder.
  • said equalizing chamber means includes at least one cylinder, each associated with a ram cylinder, said follower mean includes a piston slideably disposed in said cylinder and a piston rod rigidly attached thereto and operatively con nected to said hydraulic servo means, said rod adapted to be displaced by pressure changes in said cylinder and by the action of said hydraulic servo means.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Metal Rolling (AREA)
  • Control Of Metal Rolling (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Battery Electrode And Active Subsutance (AREA)
US343380A 1963-02-11 1964-02-07 Deformation compensating hydraulic device for rolling mills of the hydraulic mechanical pressure type Expired - Lifetime US3286495A (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR924375A FR1356340A (fr) 1963-02-11 1963-02-11 Dispositif hydraulique de compensation de cédage pour laminoir à serrage hydromécanique
BE643011A BE643011A (US06826419-20041130-M00005.png) 1963-02-11 1964-01-27
FR62716A FR90470E (fr) 1963-02-11 1966-05-24 Laminoir précontraint à serrage inversé

Publications (1)

Publication Number Publication Date
US3286495A true US3286495A (en) 1966-11-22

Family

ID=27158888

Family Applications (2)

Application Number Title Priority Date Filing Date
US343380A Expired - Lifetime US3286495A (en) 1963-02-11 1964-02-07 Deformation compensating hydraulic device for rolling mills of the hydraulic mechanical pressure type
US640972A Expired - Lifetime US3538733A (en) 1963-02-11 1967-05-24 Prestressed rolling mill with reversed clamping

Family Applications After (1)

Application Number Title Priority Date Filing Date
US640972A Expired - Lifetime US3538733A (en) 1963-02-11 1967-05-24 Prestressed rolling mill with reversed clamping

Country Status (6)

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US (2) US3286495A (US06826419-20041130-M00005.png)
BE (1) BE643011A (US06826419-20041130-M00005.png)
DE (1) DE1452005A1 (US06826419-20041130-M00005.png)
ES (1) ES339799A2 (US06826419-20041130-M00005.png)
FR (2) FR1356340A (US06826419-20041130-M00005.png)
GB (2) GB1049796A (US06826419-20041130-M00005.png)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3516273A (en) * 1966-08-16 1970-06-23 United Eng Foundry Co Strip thickness measuring device for use in a rolling mill and like apparatus
US3524495A (en) * 1967-03-01 1970-08-18 Vitaly Maximovich Niskovskikh Roller zone in the system of secondary cooling in continuous casting plants
US3527074A (en) * 1966-12-19 1970-09-08 Forges De La Loire Cie Des Ate Device for regulating the thickness of rolling-mill products,and rolling mills equipped therewith
US3538733A (en) * 1963-02-11 1970-11-10 Spidem Ste Nle Prestressed rolling mill with reversed clamping
US3538727A (en) * 1966-12-19 1970-11-10 Forges Cie Des Atel Device for regulating the thickness of rolling-mill products and rollingmills equipped therewith
US3546908A (en) * 1967-05-10 1970-12-15 British Aircraft Corp Ltd Hydraulically adjustable rolling mill having a transducer unaffected by piston deformation
US3635060A (en) * 1968-09-03 1972-01-18 Mitsubishi Heavy Ind Ltd Thrusting arrangement for a rolling mill
US4471639A (en) * 1982-11-01 1984-09-18 E. W. Bliss Company, Inc. Roll orientation control system for straightening machines
US4507996A (en) * 1982-11-15 1985-04-02 Preston Engravers, Inc. Device for transferring and monitoring load to die roll
CN110026440A (zh) * 2019-03-20 2019-07-19 宁波中超机器有限公司 用于轧机的液压压下装置及其校准方法

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1481166A (fr) * 1966-04-04 1967-05-19 Spidem Ste Nle Machine à graver par cylindres sous serrage hydraulique et avec précontrainte
DE2108783C3 (de) * 1971-02-24 1975-12-04 Nowosibirskij Metallurgitscheskij Sawod Imeni A.N. Kusmina, Nowosibirsk (Sowjetunion) Einrichtung zum automatischen Regeln der Dicke von Flachwalzgut
US3864955A (en) * 1973-12-04 1975-02-11 Blaw Knox Foundry Mill Machine Rolling mill stand

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2056409A (en) * 1933-07-10 1936-10-06 William G Ross Rolling mill
US2119390A (en) * 1936-08-26 1938-05-31 Mesta Machine Co Rolling mill
US2523553A (en) * 1946-01-29 1950-09-26 Acieries Et Forges Firminy Adjusting device for rolling mills
US2998238A (en) * 1959-09-11 1961-08-29 Lake Erie Machinery Corp Controller for the back pressure against the main ram of a press
US3075417A (en) * 1958-10-31 1963-01-29 Siderurgie Fse Inst Rech Hydraulic arrangement for adjusting the spacing of the rolls in rolling mills and for compensating mill spring

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1356340A (fr) * 1963-02-11 1964-03-27 Spidem Ste Nle Dispositif hydraulique de compensation de cédage pour laminoir à serrage hydromécanique

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2056409A (en) * 1933-07-10 1936-10-06 William G Ross Rolling mill
US2119390A (en) * 1936-08-26 1938-05-31 Mesta Machine Co Rolling mill
US2523553A (en) * 1946-01-29 1950-09-26 Acieries Et Forges Firminy Adjusting device for rolling mills
US3075417A (en) * 1958-10-31 1963-01-29 Siderurgie Fse Inst Rech Hydraulic arrangement for adjusting the spacing of the rolls in rolling mills and for compensating mill spring
US2998238A (en) * 1959-09-11 1961-08-29 Lake Erie Machinery Corp Controller for the back pressure against the main ram of a press

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3538733A (en) * 1963-02-11 1970-11-10 Spidem Ste Nle Prestressed rolling mill with reversed clamping
US3516273A (en) * 1966-08-16 1970-06-23 United Eng Foundry Co Strip thickness measuring device for use in a rolling mill and like apparatus
US3527074A (en) * 1966-12-19 1970-09-08 Forges De La Loire Cie Des Ate Device for regulating the thickness of rolling-mill products,and rolling mills equipped therewith
US3538727A (en) * 1966-12-19 1970-11-10 Forges Cie Des Atel Device for regulating the thickness of rolling-mill products and rollingmills equipped therewith
US3524495A (en) * 1967-03-01 1970-08-18 Vitaly Maximovich Niskovskikh Roller zone in the system of secondary cooling in continuous casting plants
US3546908A (en) * 1967-05-10 1970-12-15 British Aircraft Corp Ltd Hydraulically adjustable rolling mill having a transducer unaffected by piston deformation
US3635060A (en) * 1968-09-03 1972-01-18 Mitsubishi Heavy Ind Ltd Thrusting arrangement for a rolling mill
US4471639A (en) * 1982-11-01 1984-09-18 E. W. Bliss Company, Inc. Roll orientation control system for straightening machines
US4507996A (en) * 1982-11-15 1985-04-02 Preston Engravers, Inc. Device for transferring and monitoring load to die roll
CN110026440A (zh) * 2019-03-20 2019-07-19 宁波中超机器有限公司 用于轧机的液压压下装置及其校准方法
CN110026440B (zh) * 2019-03-20 2023-10-20 宁波中超机器有限公司 用于轧机的液压压下装置及其校准方法

Also Published As

Publication number Publication date
DE1452005A1 (de) 1969-10-02
GB1161715A (en) 1969-08-20
ES339799A2 (es) 1968-05-16
US3538733A (en) 1970-11-10
GB1049796A (en) 1966-11-30
BE643011A (US06826419-20041130-M00005.png) 1964-07-27
FR1356340A (fr) 1964-03-27
FR90470E (fr) 1967-12-22

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