WO2016056097A1 - 圧延機 - Google Patents
圧延機 Download PDFInfo
- Publication number
- WO2016056097A1 WO2016056097A1 PCT/JP2014/077052 JP2014077052W WO2016056097A1 WO 2016056097 A1 WO2016056097 A1 WO 2016056097A1 JP 2014077052 W JP2014077052 W JP 2014077052W WO 2016056097 A1 WO2016056097 A1 WO 2016056097A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- rolling mill
- pair
- orifice
- work roll
- hydraulic
- Prior art date
Links
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
- B21B13/02—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with axes of rolls arranged horizontally
- B21B13/023—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with axes of rolls arranged horizontally the axis of the rolls being other than perpendicular to the direction of movement of the product, e.g. cross-rolling
-
- 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
- B21B31/02—Rolling stand frames or housings; Roll mountings ; Roll chocks
-
- 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
- B21B31/18—Adjusting or positioning rolls by moving rolls axially
- B21B31/185—Adjusting or positioning rolls by moving rolls axially and by crossing rolls
-
- 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
- B21B37/007—Control for preventing or reducing vibration, chatter or chatter marks
-
- 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
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
- B21B13/02—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with axes of rolls arranged horizontally
- B21B2013/025—Quarto, four-high stands
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B2203/00—Auxiliary arrangements, devices or methods in combination with rolling mills or rolling methods
- B21B2203/18—Rolls or rollers
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B2269/00—Roll bending or shifting
- B21B2269/12—Axial shifting the rolls
- B21B2269/14—Work rolls
-
- 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
- B21B37/16—Control of thickness, width, diameter or other transverse dimensions
Definitions
- the present invention relates to an apparatus for suppressing vibration of a rolling mill, particularly a rolling mill generated during rolling of a hot rolling mill.
- Mill vibration In hot rolling, mill vibration may occur during rolling.
- Mill vibration means that the upper and lower work rolls (WR) vibrate in the horizontal direction (rolling direction) in reverse phase. Note that the reverse phase means that when the upper WR moves upstream, the lower WR moves downstream, and when the upper WR moves downstream, the lower WR moves upstream.
- Mill vibration causes fluctuations in sheet thickness, loosening of various fastening bolts of a rolling mill, vibration of pipes, and the like.
- the diameter of the orifice has been reduced as a means for further increasing the static rigidity (about ⁇ 2.0 mm or less).
- the orifice diameter is made too small, there is a limit to reducing the orifice diameter due to clogging of dust or lack of a predetermined cylinder operating speed, and in fact, a sufficient vibration suppressing effect can be obtained. There was a problem that it was not possible.
- an object of the present invention is to provide a rolling mill that can suppress mill vibration without excessively reducing the orifice diameter.
- the rolling mill according to the first invention for solving the above-mentioned problems is as follows.
- a pair of upper and lower first support means provided on one side in the rolling direction of the housing and supporting the pair of upper and lower work roll chocks;
- a pair of upper and lower second support means provided on the other rolling direction in the housing and supporting the pair of upper and lower work roll chocks;
- the first support means as a hydraulic pressing means
- the pair of upper and lower work roll chocks can be pressed in the horizontal direction, and a contraction portion and an enlargement portion are provided in the hydraulic supply / discharge pipe on the head side of the hydraulic pressing means.
- the contracted flow part is disposed closer to the hydraulic pressing means than the enlarged part,
- the inner diameter of the contracted flow portion
- a rolling mill according to a second invention that solves the above problems is as follows.
- the volume of the enlarged portion is 7% to 180% with respect to the volume of the hydraulic pressing means.
- a rolling mill according to a third invention for solving the above-described problem is In the rolling mill according to the first or second invention, An interval between the contracted flow portion and the hydraulic pressing means in the hydraulic supply / discharge pipe is 7 m or less.
- a rolling mill according to a fourth invention for solving the above-mentioned problem is as follows.
- the distance between the enlarged portion and the contracted portion in the hydraulic supply / discharge pipe is 3.5 m or less.
- the mill according to the present invention can suppress mill vibration without excessively reducing the orifice diameter.
- the rolling mill according to the present invention has found the characteristic that the damping ratio changes depending on the orifice diameter by providing an appropriate chamber, and paying attention to the dynamic stiffness obtained from the static stiffness and the damping ratio, by providing an appropriate chamber. It has been found that there is an appropriate range for the orifice diameter from the viewpoint of suppressing mill vibration. It has also been found that there is an appropriate range in the chamber capacity.
- FIG. 1 is a schematic view of a rolling mill according to Embodiment 1 of the present invention.
- the rolling mill includes a housing 11, a work roll 12, a work roll chock 13, a backup roll 14, a backup roll chock 15, a reduction means 16, a hydraulic cylinder 17 (hydraulic pressure).
- a pressing means a first support means, a housing liner 18 (second support means), a hydraulic supply / discharge pipe 19, an orifice 20 (constriction portion), a chamber 21 (enlargement portion), and a hydraulic pressure source 22.
- the pair of upper and lower work roll chocks 13 are supported by the housing 11.
- the pair of upper and lower work rolls 12 are opposed to each other, and are respectively supported by a pair of upper and lower work roll chocks 13.
- the pair of upper and lower backup rolls 14 are respectively pivotally supported by the pair of upper and lower backup roll chock 15 and face the pair of upper and lower work rolls 12, respectively.
- the reduction means 16 applies a predetermined pressure to the work roll 12 through the backup roll 14.
- the pair of upper and lower hydraulic cylinders 17 are provided on one side in the rolling direction of the housing 11 to support the pair of upper and lower work roll chock 13 and to press the pair of upper and lower work roll chock 13 in the horizontal direction.
- the pair of upper and lower housing liners 18 are provided on the other side in the rolling direction of the housing 11 and support the pair of upper and lower work roll chocks 13.
- the orifice 20 and the chamber 21 are provided in the hydraulic supply / discharge pipe 19 on the head side of the hydraulic cylinder 17 so that the orifice 20 is disposed closer to the hydraulic cylinder 17 than the chamber 21.
- the rolling mill which concerns on Example 1 of this invention may branch piping from the hydraulic supply / exhaust pipe 19 and may arrange
- the orifice diameter (inner diameter of the orifice 20) will be described.
- the rolling mill according to Embodiment 1 of the present invention focuses on increasing the horizontal dynamic rigidity of the rolling mill as suppression of mill vibration.
- This dynamic stiffness (K d ) is expressed by 2 ⁇ static stiffness (K) ⁇ damping ratio ( ⁇ ).
- FIG. 2 is a graph showing the relationship between static stiffness, damping ratio, dynamic stiffness, and orifice diameter of a conventional rolling mill.
- FIG. 3 is a graph showing the relationship between the static stiffness, damping ratio, dynamic stiffness, and orifice diameter of the rolling mill according to Example 1 of the present invention.
- FIG. 2A and FIG. 3A are graphs showing the relationship between static stiffness and orifice diameter.
- FIG. 2B and FIG. 3B are graphs showing the relationship between the damping ratio and the orifice diameter.
- FIG. 2C and FIG. 3C are graphs showing the relationship between the dynamic stiffness and the orifice diameter.
- the damping ratio is improved when the orifice diameter is increased as described above. Therefore, in this embodiment, the chamber 21 is provided, and the orifice diameter and the damping ratio, that is, the dynamic rigidity are focused on, and an appropriate range of the orifice diameter that can further increase the vibration suppression effect has been found.
- the chamber in the hydraulic supply / discharge pipe 19, the chamber is installed on the outlet side of the orifice 20, thereby generating a pressure difference and flowing oil through the orifice 20.
- the damping ratio can be improved.
- the dynamic rigidity of the chamber 21 is particularly improved when the capacity is set within a predetermined range (described later) from the viewpoint of the dynamic rigidity.
- FIG. 4 is a simulation model diagram of dynamic stiffness.
- A is the orifice 20
- B is the hydraulic supply / discharge pipe 19
- K1 is the spring constant of the housing
- K is the static rigidity of the entire model
- c is the damping coefficient of the structure
- D is the housing 11
- E is the work roll 12.
- F is a hydraulic cylinder 17
- P is a hydraulic pump.
- the equation of motion of the work roll 12 and the work roll chock 13 and the orifice 20 incorporate the characteristic that the flow rate is determined by the pressure difference.
- the dynamic stiffness K d gives an excitation force f 0 for each excitation frequency ⁇ , and is expressed as the minimum value of the ratio between the excitation force f 0 and the work roll displacement X, and is a value that determines the movement during vibration.
- FIG. 7A is a graph showing the relationship between the orifice diameter and the dynamic stiffness ratio
- FIG. 7B shows the ratio of the orifice diameter to the inner diameter of the hydraulic supply / discharge pipe 19 (ratio of the orifice diameter to the pipe inner diameter); It is a graph which shows the relationship with dynamic rigidity ratio.
- FIG. 7A shows the case where the inner diameter (pipe inner diameter) of the hydraulic supply / discharge pipe 19 is ⁇ 18 mm.
- the dynamic stiffness ratio refers to the ratio to the dynamic stiffness when the orifice diameter is 0, that is, when the hydraulic cylinder is completely closed (the same applies to FIGS. 8 to 9).
- the dynamic stiffness ratio is further improved by designing the orifice diameter, which was conventionally designed to be about ⁇ 2.0 mm or less, on the contrary.
- the inflection points are present at orifice diameters of 2.5 mm and 15 mm, and the dynamic stiffness ratio increases sharply at 2.5 mm or more and 15 mm or less.
- the pipe inner diameter ratio has inflection points at 0.15 (15%) and 0.85 (85%), and the dynamic rigidity ratio rises sharply at 15% or more and 85% or less.
- the orifice diameter is 2.5 mm or more and the pipe inner diameter ratio is 15% to 85%.
- the dynamic stiffness ratio is improved to 1.2 or more.
- FIG. 8A is a graph showing the relationship between the capacity of the chamber 21 (chamber volume) and the dynamic stiffness ratio
- FIG. 8B shows the ratio of the chamber volume to the volume of the hydraulic cylinder 17 (cylinder volume of the chamber volume). Ratio) and the dynamic stiffness ratio.
- the cylinder volume was defined by the capacity determined by the cylinder diameter and stroke.
- the hydraulic cylinder size is D250 mm (head diameter) / d230 mm (rod diameter) ⁇ 90 mm stroke
- the cylinder volume Vc ( ⁇ / 4) ⁇ 25 2 ⁇ 9 (cm 3 ), which is about 4.4.
- the chamber volume is 0.3 liter to 8.0 liter
- the cylinder volume ratio of the chamber volume is 0.07 to 1.8.
- the dynamic stiffness ratio is improved to 1.2 or more and a maximum of about 3.0. That is, as shown in FIG. 8B, when the cylinder volume ratio of the chamber volume is 0.07 or more, the dynamic rigidity ratio is improved to 1.2 or more and about 3.0 at the maximum.
- the cylinder volume ratio of the chamber volume is set to 0.07 or more and 1.8 or less (that is, 7% or more and 180% or less). At this time, the dynamic stiffness ratio is 1.2 or more.
- the distance between the cylinder and the orifice is set to 7.0 m or less.
- the distance between the orifice and the chamber is set to 3.5 m or less.
- Example 1 of the present invention has been described above.
- the orifice 20 and the chamber 21 are provided only on the head side of the hydraulic supply / discharge pipe 19 in FIGS. May be. Further, only the orifice may be provided on the rod side of the hydraulic supply / discharge pipe 19 and the chamber may not be provided. In any case, the effect of the orifice 20 and the chamber 21 is not changed.
- the rolling mill according to Example 1 of the present invention can suppress mill vibration without reducing the orifice diameter by using the above-described configuration.
- the present invention is suitable as an apparatus for suppressing vibration of a rolling mill, particularly a rolling mill generated during rolling of a hot rolling mill.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Control Of Metal Rolling (AREA)
- Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
Abstract
Description
ハウジングと、
前記ハウジングに支持された、上下一対のワークロールチョックと、
前記上下一対のワークロールチョックにそれぞれ軸支された、互いに対向する上下一対のワークロールと、
前記ワークロールに所定圧力を作用させる圧下手段と、
前記ハウジングにおける圧延方向一方に設けられて前記上下一対のワークロールチョックを支持する上下一対の第1支持手段と、
前記ハウジングにおける圧延方向他方に設けられて前記上下一対のワークロールチョックを支持する上下一対の第2支持手段とを備え、
前記第1支持手段を油圧式押圧手段として、前記上下一対のワークロールチョックを水平方向に押圧可能とすると共に、該油圧式押圧手段のヘッド側の油圧給排管に縮流部及び拡大部を設け、該縮流部が該拡大部よりも該油圧式押圧手段側に配置され、
前記縮流部の内径を、φ2.5mm以上、かつ、前記油圧給排管の内径に対し15%~85%の大きさとする
ことを特徴とする。
上記第1の発明に係る圧延機において、
前記拡大部の体積を、前記油圧式押圧手段の体積に対し7%~180%とする
ことを特徴とする。
上記第1又は2の発明に係る圧延機において、
前記油圧給排管における前記縮流部と前記油圧式押圧手段との間隔を7m以下とする
ことを特徴とする。
上記第1から3のいずれか1つの発明に係る圧延機において、
前記油圧給排管における前記拡大部と前記縮流部との間隔を3.5m以下とする
ことを特徴とする。
本発明の実施例1に係る圧延機について、まず、図1を用いて説明する。図1は、本発明の実施例1に係る圧延機の概略図である。
12 ワークロール
13 ワークロールチョック
14 バックアップロール
15 バックアップロールチョック
16 圧下手段
17 油圧シリンダ
18 ハウジングライナ
19 油圧給排管
20 オリフィス
21 チャンバ
22 油圧源
Claims (4)
- ハウジングと、
前記ハウジングに支持された、上下一対のワークロールチョックと、
前記上下一対のワークロールチョックにそれぞれ軸支された、互いに対向する上下一対のワークロールと、
前記ワークロールに所定圧力を作用させる圧下手段と、
前記ハウジングにおける圧延方向一方に設けられて前記上下一対のワークロールチョックを支持する上下一対の第1支持手段と、
前記ハウジングにおける圧延方向他方に設けられて前記上下一対のワークロールチョックを支持する上下一対の第2支持手段とを備え、
前記第1支持手段を油圧式押圧手段として、前記上下一対のワークロールチョックを水平方向に押圧可能とすると共に、該油圧式押圧手段のヘッド側の油圧給排管に縮流部及び拡大部を設け、該縮流部が該拡大部よりも該油圧式押圧手段側に配置され、
前記縮流部の内径を、φ2.5mm以上、かつ、前記油圧給排管の内径に対し15%~85%の大きさとする
ことを特徴とする圧延機。 - 前記拡大部の体積を前記油圧式押圧手段の体積に対し7%~180%とする
ことを特徴とする、請求項1に記載の圧延機。 - 前記油圧給排管における前記縮流部と前記油圧式押圧手段との間隔を7m以下とする
ことを特徴とする、請求項1又は2に記載の圧延機。 - 前記油圧給排管における前記拡大部と前記縮流部との間隔を3.5m以下とする
ことを特徴とする、請求項1から3のいずれか1項に記載の圧延機。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP14903624.6A EP3205417B1 (en) | 2014-10-09 | 2014-10-09 | Rolling mill |
KR1020177004801A KR101908872B1 (ko) | 2014-10-09 | 2014-10-09 | 압연기 |
CN201480082485.1A CN107000002B (zh) | 2014-10-09 | 2014-10-09 | 轧机 |
JP2016552761A JP6345262B2 (ja) | 2014-10-09 | 2014-10-09 | 圧延機 |
PCT/JP2014/077052 WO2016056097A1 (ja) | 2014-10-09 | 2014-10-09 | 圧延機 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2014/077052 WO2016056097A1 (ja) | 2014-10-09 | 2014-10-09 | 圧延機 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2016056097A1 true WO2016056097A1 (ja) | 2016-04-14 |
Family
ID=55652753
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2014/077052 WO2016056097A1 (ja) | 2014-10-09 | 2014-10-09 | 圧延機 |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP3205417B1 (ja) |
JP (1) | JP6345262B2 (ja) |
KR (1) | KR101908872B1 (ja) |
CN (1) | CN107000002B (ja) |
WO (1) | WO2016056097A1 (ja) |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH02151310A (ja) * | 1988-12-05 | 1990-06-11 | Sumitomo Light Metal Ind Ltd | 圧延機における振動防止装置 |
JP2001113308A (ja) * | 1999-08-11 | 2001-04-24 | Mitsubishi Heavy Ind Ltd | 圧延機 |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN85101137B (zh) * | 1985-04-01 | 1988-01-06 | 株式会社日立制作所 | 轧机 |
JPS61259810A (ja) * | 1985-05-10 | 1986-11-18 | Ishikawajima Harima Heavy Ind Co Ltd | 圧延方法及び装置 |
JPH04190904A (ja) * | 1990-11-22 | 1992-07-09 | Ube Ind Ltd | 圧延機 |
JP2004314089A (ja) * | 2003-04-11 | 2004-11-11 | Ishikawajima Harima Heavy Ind Co Ltd | ロールギャップの調整装置及び調整方法、圧延機及び圧延方法 |
FR2869819B1 (fr) * | 2004-05-07 | 2006-08-04 | Vai Clecim Soc Par Actions Sim | Procede et dispositif d'amortissement d'une cage de laminoir |
WO2008001466A1 (fr) * | 2006-06-30 | 2008-01-03 | Mitsubishi-Hitachi Metals Machinery, Inc. | Laminoir |
CN202539185U (zh) * | 2011-11-23 | 2012-11-21 | 西安曼海特工业技术有限公司 | 一种薄钢板轧机的防震动装置 |
-
2014
- 2014-10-09 JP JP2016552761A patent/JP6345262B2/ja active Active
- 2014-10-09 WO PCT/JP2014/077052 patent/WO2016056097A1/ja active Application Filing
- 2014-10-09 EP EP14903624.6A patent/EP3205417B1/en active Active
- 2014-10-09 KR KR1020177004801A patent/KR101908872B1/ko active IP Right Grant
- 2014-10-09 CN CN201480082485.1A patent/CN107000002B/zh active Active
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH02151310A (ja) * | 1988-12-05 | 1990-06-11 | Sumitomo Light Metal Ind Ltd | 圧延機における振動防止装置 |
JP2001113308A (ja) * | 1999-08-11 | 2001-04-24 | Mitsubishi Heavy Ind Ltd | 圧延機 |
Non-Patent Citations (1)
Title |
---|
See also references of EP3205417A4 * |
Also Published As
Publication number | Publication date |
---|---|
KR101908872B1 (ko) | 2018-10-16 |
KR20170033408A (ko) | 2017-03-24 |
EP3205417B1 (en) | 2019-09-04 |
EP3205417A1 (en) | 2017-08-16 |
CN107000002A (zh) | 2017-08-01 |
EP3205417A4 (en) | 2018-06-27 |
JPWO2016056097A1 (ja) | 2017-04-27 |
CN107000002B (zh) | 2019-08-27 |
JP6345262B2 (ja) | 2018-06-20 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
KR20070042507A (ko) | 압연스탠드 충격흡수방법 및 충격흡수장치 | |
US6510721B1 (en) | Rolling mill | |
CA2954502C (en) | Rolling mill third octave chatter control by process damping | |
WO2007035289A3 (en) | Machine to produce expanded metal spirally lock-seamed tubing from solid coil stock | |
Heidari et al. | Effect of friction on tandem cold rolling mills chattering | |
JP6345262B2 (ja) | 圧延機 | |
Amabili et al. | Vibrations of circular cylindrical shells with nonuniform constraints, elastic bed and added mass. Part III: Steady viscous effects on shells conveying fluid | |
JP4679642B2 (ja) | 圧延機 | |
JP2011050969A (ja) | 減衰強化型圧延機 | |
JP2018532597A (ja) | ロールスタンド内の振動を減衰させるためのロールスタンド、圧延設備及び方法 | |
TWM574102U (zh) | 拆卸裝置 | |
CN105855296A (zh) | 一种液压缸非线性刚度约束下的轧机辊系稳定性控制方法 | |
Huang et al. | Influence of asymmetric structure parameters on rolling mill stability | |
JP5527238B2 (ja) | 金属板材の厚板圧延機 | |
Lang et al. | The effect of the key process parameters in the innovative hydroforming on the formed parts | |
JP2018065079A (ja) | 塗工装置 | |
CN204770028U (zh) | 具有降温保油功能的卷板机 | |
Savage | Meniscus roll coating: Steady flows and instabilities | |
CN109578650A (zh) | 一种便于进行固定的液压阀 | |
CN202516848U (zh) | 四辊冷轧机除油装置 | |
Liu et al. | Research on the pipeline influence on the dynamic characteristics of a hydraulic servo system based on Hypneu | |
Liu et al. | Study on the Influence of Dynamic Characteristics of Servo Valve on Coupling Vibration of Cold Rolling Mill | |
JP2009045635A (ja) | 圧延材の張力制御方法及び圧延装置 | |
Kim et al. | The Effect of Rolling Speed and Friction on Cold Rolling Mill Stability | |
JP2014161894A (ja) | 差厚鋼板の製造装置および製造方法 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 14903624 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2016552761 Country of ref document: JP Kind code of ref document: A |
|
ENP | Entry into the national phase |
Ref document number: 20177004801 Country of ref document: KR Kind code of ref document: A |
|
REEP | Request for entry into the european phase |
Ref document number: 2014903624 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2014903624 Country of ref document: EP |
|
NENP | Non-entry into the national phase |
Ref country code: DE |