EP2274118B1 - Laminoir circulaire avec rouleau de conformation - Google Patents

Laminoir circulaire avec rouleau de conformation Download PDF

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Publication number
EP2274118B1
EP2274118B1 EP09731268A EP09731268A EP2274118B1 EP 2274118 B1 EP2274118 B1 EP 2274118B1 EP 09731268 A EP09731268 A EP 09731268A EP 09731268 A EP09731268 A EP 09731268A EP 2274118 B1 EP2274118 B1 EP 2274118B1
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EP
European Patent Office
Prior art keywords
rolling mill
pinion
support
frame
roller
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Active
Application number
EP09731268A
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German (de)
English (en)
French (fr)
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EP2274118A1 (fr
Inventor
Guy Vinzant
Alain Kaczorek
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Individual
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Individual
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21H—MAKING PARTICULAR METAL OBJECTS BY ROLLING, e.g. SCREWS, WHEELS, RINGS, BARRELS, BALLS
    • B21H1/00—Making articles shaped as bodies of revolution
    • B21H1/06—Making articles shaped as bodies of revolution rings of restricted axial length

Definitions

  • the invention relates to a circular rolling mill for forming annular pieces, such as forged wheel or pulley blanks or the like.
  • the invention provides more particularly to provide a circular rolling mill whose operation is reliable and whose maintenance can be lightened without harming the quality of the rolling obtained or the strength of the rolling mill.
  • the invention relates to a circular rolling mill for the conformation of annular pieces, this rolling mill comprising a pair of rollers, respectively internal and external, capable of shaping the radial inner and outer faces of a workpiece, as well as a pair tapered rollers, respectively upper and lower, able to shape the front faces of this piece.
  • This mill also comprises means for moving at least some of these rollers relative to a frame.
  • This rolling mill is characterized in that the means for moving at least one of the rolls comprise at least a pinion and at least one rack integral with a member for moving the roller, in that the pinion is rotated by the output shaft of an electric geared motor mounted on a support articulated with respect to the frame around the axis of rotation of the pinion and in that damping means are provided to damp the pivoting of the support about its hinge axis.
  • the transmission of effort between the electric gear motor and the shaping roll or conformation roll is obtained reliably, including under heavy load, thanks to the use of a pinion type connection / rack.
  • the fact that the geared motor is mounted on a hinged support relative to the frame of the rolling mill allows that, in case of irregularity of the surface with which the roller interacts, the transient overload transmitted to the rack because of this irregularity can be reported without damage to the pinion, while it tends to rotate in a direction opposite to that normally imposed by the geared motor.
  • the damping means allow to absorb the corresponding energy, without too much stress of the motor-reducer.
  • the rolling mill 1 shown on Figures 1 to 7 comprises a main frame 2 on which is mounted a radial cage 3 fixed relative to the frame 2 and an axial cage 4 movable parallel to a longitudinal axis X 2 of the frame 2.
  • the cage 3 carries a circular cylindrical roller 10 rotatably mounted around a vertical axis Z 10 and rotated by a main electric motor 11.
  • the cage 3 also carries a secondary roller or mandrel 12 rotatably mounted about an axis Z 12 parallel to the axis Z 10 inside a mobile column 13, with respect to a main part 31 of the cage 3, parallel to the X axis 2 .
  • the column 13 is supported by two bars 14 and 15 capable of sliding by Part 31, as can be seen from the following explanations.
  • the cage 3 also comprises a plate 16 which defines a housing 17 for receiving the lower end of the mandrel 12 when the column 13 and the plate 16 are aligned vertically, that is to say when the axis Z 12 passes through the center of the housing 17. It is then possible to lower the mandrel 12 to engage partially in the housing 17.
  • the plate 16 is supported by two bars 18 and 19 which extend parallel to the bars 14 and 15 and to the axis X 2 .
  • the mill 1 also comprises a lower conical roller 20 supported by the axial cage 4 and driven in rotation by an electric motor 21.
  • the cage 4 also supports an upper conical roller 22 rotated by an electric motor 23.
  • the roll 20 is supported by the frame 41 of the axial cage 4 with its axis A 20 fixed with respect to this frame.
  • the roller 20 can only rotate about the axis A 20 .
  • the roller 22 is supported relative to the frame 41 with a possibility of displacement in vertical translation, parallel to the axes Z 10 and Z 12 , as represented by the double arrow F 3 at the figure 2 .
  • This possibility of vertical displacement of the axis A 22 allows the roller 22 to exert on the upper end face 103 of the part 100 a force F 4 directed towards the roller 20.
  • This has the effect of inducing a reaction force F 5 of the roll 20 on the lower end face 104 of the workpiece 100.
  • the roller 22 is mounted on a carriage 24 equipped with two racks 25 and 26 arranged vertically, that is to say parallel to the direction of the double arrow F 3 .
  • the carriage 24 is slidably mounted relative to bars 42 forming the frame frame 41 and which are visible to the figures 5 and 6 where the dressing of the frame 41 is not shown. Note in these figures that the carriage 24 actually carries four racks, namely two racks 25 and 26 disposed on the carriage 24 substantially above the roller 22 and two racks 27 and 28 located on the other side of the frame 41 by report to the roll 22.
  • Two pinions 51 and 52 are mounted on a shaft 53 which extends parallel to the axis X 2 .
  • the pinions 51 and 52 are respectively engaged with the racks 25 and 27.
  • the shaft 53 constitutes the output shaft of a geared motor 61 consisting of an electric motor 62 and a reversible gear 63 connected by a Angle gear 64 to 90 °.
  • two pinions 54 and 55 are mounted on a shaft 56 and are respectively engaged with the teeth 26 and 28.
  • the shaft 56 constitutes the output shaft of a geared motor 66 comprising an electric motor 67 , a reversible reducer 68 and an angle gear 69 at 90 °.
  • each geared motor 61 or 66 supports the engine and associated bevel gear.
  • the gearbox 63 is mounted on a reaction arm 71 hinged to the frame 41 about the longitudinal axis X 53 of the shaft 53, which forms the axis of rotation of the gears 51 and 52 and which is parallel to the axis X 2 .
  • the gearbox 68 is mounted on a reaction arm 72 forming a support and articulated with respect to the frame 41 about the longitudinal axis X 56 of the shaft 56, which forms the axis of rotation of the gears 54 and 55 and which is parallel to the axes X 53 and X 2 .
  • the geared motors 61 and 66 are supported by the arms 71 and 72 respectively through the gearboxes 63 and 68.
  • the arm or support 71 is connected by a connecting rod 73 to a shock absorber 74.
  • the articulated support 72 is connected by a connecting rod 75 to a shock absorber 76.
  • the dampers 74 and 76 are mounted head-to-tail and fixed in the upper part of the frame 41, generally in a horizontal direction perpendicular to the axis X 2 .
  • the various electric motors of the rolling mill 1 are controlled by an electronic unit 200 represented schematically only at the figure 2 and connected to the rolling mill 1 by a cable bundle 201.
  • the unit 200 coordinates the movements of the various geared motors of the rolling mill 1, for example geared motors 61 and 66, to ensure the effective vertical translation of the carriage 24.
  • the various motors and geared motors are controlled by the unit 200 according to a predetermined rolling range. This has the effect of exerting, on the surfaces 101 to 104 of the part 100 to be treated and by means of the conformation rollers 10, 12, 20 and 22, the conformational forces F 1 , F 2 , F 4 and F 5 .
  • the rotation of the shafts 53 and 56 by the geared motors 61 and 66 makes it possible to exert on the carriage 24 a vertical force F 10 , parallel to the axes Z 10 and Z 12 , which is transmitted to the roller 22 to create the effort F 4 and, by reaction of the roller 20, the force F 5 on the faces 103 and 104.
  • the faces 103 and 104 are normally flat and regular. It is possible, however, that these surfaces have a protruding irregularity, especially following a stoppage of the rolling mill.
  • the height of the workpiece 100 between the rollers 20 and 22 can increase sharply. This tends to raise the carriage 24 relative to the frame 41, inducing, by a corresponding movement of the racks 25 to 28, a rotational movement of the gears 51, 52, 54 and 55 in a direction opposite to the torque exerted by the motorcycle
  • the inverted rotation movement of the pinions is transmitted to the shafts 53 and 56.
  • the damper 74 comprises a rod 81 integral with a piston 82 mounted inside a body 83 common to the two dampers 74 and 76.
  • the connecting rod 73 is articulated on the rod 81, so that the pivoting of the rod reaction arm 71 about the X axis 53 relative to the frame 41 has the effect of moving the piston 82 inside the body 83, to the left on the figure 4 .
  • the points of articulation of the connecting rod 73 on the arm 71, on the one hand, and on the rod 81, on the other hand, are defined so that the pivoting movement of the arm 71 about the X axis 53 , which takes place in the direction of arrow F 6 to Figures 4 and 6 , has the effect of moving the piston 81 in a direction of reducing the volume of a chamber 84 defined inside the body 83 and in which is disposed a stack 85 of Belleville washers.
  • the crushing of the stack of washers 85 makes it possible to damp the pivoting movement of the arm 71 in the direction of the arrow F 6 .
  • two Belleville washers 87 are also arranged, which make it possible to damp the return of the arm 71 towards its normal position when the counterforce, due to the unevenness of the surface 100, is supported by geared motors 61 and 66.
  • a motion detector 91 which is shown only at the figure 4 for clarity of the drawing, is associated with the damper 74 and connected to a folded sheet 92 fixed on the rod 81 and whose movement is processed by the detector 91 to emit a corresponding signal S 1 , in the direction of the unit 200
  • the signal S 1 is transmitted to the unit 200 which can be programmed to slow down then the speed of rotation of the rollers 10, 12, 20 and 22 until the return of the arms 71 to its normal position which is also dictated by the detector 91.
  • the shape of the detector 91 and the sheet 92 shown in FIG. figure 4 is very schematic.
  • any type of suitable detector can be used in conjunction with the damper 74, for example a detector with measuring ruler, a potentiometer detector or a Hall effect detector.
  • the damper 76 has a structure similar to that of the damper 74 and is not described in more detail. It is also associated with an unrepresented displacement sensor.
  • the mode of controlling the vertical displacement of the roller 22 is also implemented for the horizontal displacement of the mandrel or inner roller 12.
  • the bars 14, 15, 18 and 19 are each equipped with a rack.
  • the rack 125 of the bar 18 is engaged with a pinion 151 mounted on the output shaft 153 of a geared motor 161 comprising an electric motor 162 and a reducer 163.
  • X 153 is noted the longitudinal axis of the shaft 153 which forms the axis of rotation of the pinion 151.
  • the geared motor 161 is mounted on a reaction arm 171 articulated on the main part 31 of the cage 3, about the axis X 153 .
  • the rack 127 of the bar 14 is visible at the figure 8 , as well as the pinion 154 associated with this rack.
  • Pinion 154 is driven by a geared motor 166 whose 156 output shaft.
  • the longitudinal axis X 156 of the shaft 156 forms the axis of rotation of the pinion 154.
  • the geared motor 166 is mounted on a reaction arm 172 hinged about the portion 31 about the axis X 156 which is vertical.
  • the reaction arms 171 and 172 are respectively associated with dampers 174 and 176.
  • the bars 15 and 19 are also equipped with racks, respectively 127 'and 125', each with a pinion 154 'and 151'.
  • These pinions are each driven by a geared motor 161 'or 166' supported by a reaction arm 171 ', 172' articulated on the main part 31 of the cage 3 about a longitudinal axis X 153 ', X 156 ' of the output shaft 153 'or 156' of these geared motors which form the axes of rotation of the gears 151 'and 154'.
  • the unit 200 coordinates the operation of the geared motors 161, 161 ', 166 and 166' to ensure the effective horizontal translation of the carriage formed of the subassemblies 13 to 19.
  • the geared motors 161, 161 ', 166 and 166' make it possible to exert, on the bars 14, 15, 18 and 19 of the carriage constituted by the elements 13 to 19, a force directed towards the roll 10, that is to say opposite the cage 4, and equal to the sum of the tensile forces T 1 and T 2 .
  • This tensile force tends to bring the mandrel 12 of the roll 10 in translation parallel to the axis X 2 , which makes it possible to exert the shaping forces F 1 and F 2 on the faces 101 and 102 of the piece 100.
  • irregularity case on one of these surfaces especially at the beginning of the rolling process where the blank is relatively irregular, the mandrel 12, the column 13 and the plate 16 can be pushed temporarily towards the central axis Z 100 of the piece 100. This is possible due to the pivoting of one or more of the reaction arms 171, 171 ', 172 and 172' around their respective axes of articulation on the portion 31. This articulation movement is damped by the dampers 174, 174 ', 176 and 176'.
  • this pivoting movement of the reaction arms 171, 171 ', 172 and 172' makes it possible to absorb the antagonistic pairs which are exerted on the shafts 153, 153 ', 156 and 156 for driving sprockets 151, 151 ', 154 and 154'.
  • the rolling mill 1 is also provided with centering arms 200 and 202 each equipped with a roller 220 or 222 intended to bear against the surface 101 of the part 100 during rolling.
  • the elements 200 and 220 are not represented in the figure 2 , for the sake of clarity.
  • the centering arm 200 is displaced towards the central axis Z 100 of the part 100 during rolling by means of an electric gear motor 261 whose output shaft 253 is equipped with a pinion 251 which meshes with a another pinion 281, fixed on the arm 200.
  • a geared motor 266 has its output shaft 256 equipped with a pinion 254 which meshes with a second pinion 284 fixed on the arm 202.
  • Each geared motor 261 or 266 is mounted on a support 271 or 272 in the form of a reaction arm articulated on the portion 31 around the longitudinal axis X 253 or X 256 of the output shaft 253 or 256 corresponding to this motorcycleshrinkers 274 and 276 similar to those mentioned for the control of the vertical position of the roller 22, are used to damp the pivoting movements of the reaction arms 271 and 272 around their respective axes of articulation. These pivoting movements may result from irregularities in the surface 101 and are absorbed without damage to the gears 251, 281, 254 and 284 and the geared motors 261 and 266.
  • dampers 74, 76, 174, 174 ', 176, 176', 274 and 276 used to absorb the energy due to the pivoting of the different reaction arms are identical. . This is not required, however.
  • the pivoting of the reaction arms 171, 171 ', 172, 172', 271 and 272 can be detected, as explained about the pivoting of the reaction arms 71 and 72.
  • the detection of the pivoting of the arms 171, 171 ', 172, 172 ', 271 and 272 can be used, as explained with reference to the detector 91, to signal a surface irregularity to the unit 200 which can then adapt the operation of the mill 1.
  • a sensor of the detector type 91 is associated with each arm 171, 171 ', 172, 172', 271 and 272.
  • the unit 200 can control the geared motors which cooperate to drive the same roll in a coordinated manner. For example, when the detector 91 associated with the damper 74 has detected pivoting of the arm 71 about the X axis 53 , the unit 200 is informed by the signal S 1 . Taking account of this signal, the unit 200 can control the geared motor 66 so that it actuates the shaft 56 so as to compensate, at the pinions 54 and 55 and the racks 26 and 28, the angular offset which occurred around the X axis 53 . This ensures the equilibrium of the vertical forces exerted on the carriage 24 by the different sets of gears / racks.
  • the unit 200 can drive geared motors other than that supported by the reaction arm whose pivoting has been detected to compensate for the possible imbalance in the drive of the column 13 or the plate 16. This ensures that the mandrel 12 and housing 17 are permanently correctly aligned and that the carriage 13-19 is not subject to efforts that could distort it. This coordination of the action of the geared motors is possible because the articulated reaction arms and the associated detectors rapidly detect the irregularities of the part to be treated.
  • each of the carriages 13-19 or 24 of horizontal or vertical displacement of the rollers 12 or 22 carries four racks 25 to 28, 125, 127 or equivalent which each cooperate with a pinion 51, 52, 54 , 55, 151 or equivalent. This allows to restart the sudden efforts by these carts.
  • the invention has been shown during its implementation for the control of the position of the conformation rollers 12 and 22. It can be implemented only for the control of only one of these conformation rollers. Similarly, its implementation for controlling the centering arms 200 and 202 is optional.
  • the cage 4 is equipped with a gear motor 461 which drives a pinion 451 engaged with a rack 462 which extends on the main frame 2 parallel to the axis X 2 . It is thus possible to control the position of the axial cage 4 along the axis X 2 .
  • the geared motor 461 is supported by a reaction arm 471 hinged to the frame 41 of the cage 4 about an axis parallel to the output axis of the geared motor 461.
  • damping means constituted by piston dampers and stacking Belleville washers.
  • Other types of dampers are conceivable, such as compression coil spring dampers, gas dampers or dampers with elastomer block.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Crushing And Grinding (AREA)
  • Transmission Devices (AREA)
  • Discharging, Photosensitive Material Shape In Electrophotography (AREA)
  • Rolls And Other Rotary Bodies (AREA)
EP09731268A 2008-03-21 2009-03-20 Laminoir circulaire avec rouleau de conformation Active EP2274118B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0851834A FR2928850B1 (fr) 2008-03-21 2008-03-21 Laminoir circulaire avec rouleau de conformation
PCT/FR2009/050474 WO2009125102A1 (fr) 2008-03-21 2009-03-20 Laminoir circulaire avec rouleau de conformation

Publications (2)

Publication Number Publication Date
EP2274118A1 EP2274118A1 (fr) 2011-01-19
EP2274118B1 true EP2274118B1 (fr) 2011-10-12

Family

ID=39865020

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09731268A Active EP2274118B1 (fr) 2008-03-21 2009-03-20 Laminoir circulaire avec rouleau de conformation

Country Status (8)

Country Link
US (1) US8683838B2 (zh)
EP (1) EP2274118B1 (zh)
KR (1) KR101541943B1 (zh)
CN (1) CN102036767B (zh)
AT (1) ATE528085T1 (zh)
ES (1) ES2374793T3 (zh)
FR (1) FR2928850B1 (zh)
WO (1) WO2009125102A1 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017008449A1 (de) * 2017-09-08 2019-03-14 Schuler Pressen Gmbh Radial-Axial-Ringwalzwerk zum Walzen eines Ringes

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
PL3177419T3 (pl) * 2014-08-08 2020-08-24 Muraro S.R.L. Maszyna do, i sposób kształtowania elementów pierścieniowych, jak na przykład, walcarka do, i sposób obiegowego walcowania elementów pierścieniowych
CN105522081B (zh) * 2016-01-18 2018-07-27 山西双环重工集团有限公司 碾环机活动托料架
KR101852265B1 (ko) * 2016-09-30 2018-04-25 김영수 링 성형용 냉간 압연 장치
EP3300814A1 (fr) * 2016-09-30 2018-04-04 Forge Pat GmbH Laminoir circulaire avec rouleaux de conformation et procédé de contrôle de la position d'un rouleau d'un tel laminoir
KR102162180B1 (ko) * 2018-10-22 2020-10-08 칼텍(주) 연속 성형용 링 압연 장치
KR102149757B1 (ko) * 2018-10-31 2020-08-31 최원중 유압 기반의 자동운전식 버 방지용 수직형 고정밀 핫롤링 머신
CN109848340B (zh) * 2018-12-29 2020-06-12 广东毅马集团有限公司 一种碾环机结构
CN116078961B (zh) * 2023-04-07 2023-06-16 山西天宝集团有限公司 一种新能源风力发电t.l型法兰的碾环装置
CN116078960B (zh) * 2023-04-07 2023-06-02 山西天宝集团有限公司 一种适用于t型和l型法兰生产加工用碾环装置

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DE1752887C3 (de) * 1968-07-31 1974-06-06 J. Banning Ag, 4700 Hamm Vierwalzen-Ringwalzwerk
DE2634625A1 (de) * 1976-07-31 1978-02-02 Banning Ag J Ringwalzwerk
DE2923001A1 (de) * 1979-06-07 1981-01-22 Thyssen Industrie Ringwalzmaschine mit dornwalzen- revolverkopf
US4869088A (en) * 1988-07-05 1989-09-26 Kazuo Kadotani Ring shaping apparatus
DE4421596C2 (de) * 1994-06-21 1998-01-15 Bad Dueben Profilwalzmaschinen Ringwalzmaschine mit Dämpfungseinrichtung
CN2412677Y (zh) * 1998-07-14 2001-01-03 沈芝蓉 辗环机
US7748308B2 (en) * 2005-09-26 2010-07-06 Unico, Inc. Pneumatic biasing of a linear actuator and implementations thereof

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017008449A1 (de) * 2017-09-08 2019-03-14 Schuler Pressen Gmbh Radial-Axial-Ringwalzwerk zum Walzen eines Ringes
US11077482B2 (en) 2017-09-08 2021-08-03 Schuler Pressen Gmbh Radial/axial ring rolling mill for rolling a ring

Also Published As

Publication number Publication date
FR2928850A1 (fr) 2009-09-25
ES2374793T3 (es) 2012-02-22
FR2928850B1 (fr) 2010-04-02
KR20100125429A (ko) 2010-11-30
CN102036767A (zh) 2011-04-27
US20110138871A1 (en) 2011-06-16
US8683838B2 (en) 2014-04-01
CN102036767B (zh) 2013-06-05
ATE528085T1 (de) 2011-10-15
KR101541943B1 (ko) 2015-08-05
WO2009125102A1 (fr) 2009-10-15
EP2274118A1 (fr) 2011-01-19

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