JP6345262B2 - Rolling mill - Google Patents

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JP6345262B2
JP6345262B2 JP2016552761A JP2016552761A JP6345262B2 JP 6345262 B2 JP6345262 B2 JP 6345262B2 JP 2016552761 A JP2016552761 A JP 2016552761A JP 2016552761 A JP2016552761 A JP 2016552761A JP 6345262 B2 JP6345262 B2 JP 6345262B2
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pair
work roll
rolling mill
hydraulic
lower work
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JPWO2016056097A1 (en
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古元　秀昭
秀昭 古元
林　寛治
寛治 林
佐古　彰
彰 佐古
正 日浦
正 日浦
英樹 戸中
英樹 戸中
金森　信弥
信弥 金森
大楽 孫
大楽 孫
群 範
群 範
福臣 王
福臣 王
国華 徐
国華 徐
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Primetals Technologies Japan Ltd
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    • 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

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Metal Rolling (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)

Description

本発明は、圧延機、特に熱間圧延機の圧延中に発生する圧延機の振動を抑制する装置に関する。   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.

熱間圧延は、圧延中にミル振動が発生することがある。ミル振動とは、上下のワークロール（ＷＲ）が逆相にて水平方向（圧延方向）に振動することを指す。なお、逆相とは、上ＷＲが上流側に動けば下ＷＲは下流側に動き、反対に上ＷＲが下流側に動けば下ＷＲは上流側に動くことである。ミル振動は、板厚の変動や圧延機の各種の締結ボルトの緩みや配管振動などの原因となる。   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.

従来は、静剛性に着目して振動を抑制していた。すなわち、従来は、圧延機のハウジングとワークロールチョックとの隙間を油圧シリンダで押圧して無くし、水平方向の静剛性を上げるように考えており、さらに、その延長線上で、油圧シリンダの油圧給排管に設けたオリフィス（下記特許文献１参照）の径（オリフィス径）を小さくして静剛性を上げていた。   Conventionally, vibration has been suppressed focusing on static rigidity. That is, conventionally, it has been considered that the gap between the housing of the rolling mill and the work roll chock is eliminated by pressing with a hydraulic cylinder to increase the static rigidity in the horizontal direction. The static rigidity was increased by reducing the diameter (orifice diameter) of the orifice (see Patent Document 1 below) provided in the pipe.

特開２００１−１１３３０８号公報JP 2001-113308 A

上述のように、従来は静剛性をより上げる手段としてオリフィス径を小さくしていた（約φ２．０ｍｍ又はそれ以下）。しかし、オリフィス径を小さくし過ぎると、ゴミが詰まったり、所定のシリンダ動作速度がでない等のために、オリフィス径を小さくするにも限界があり、実際には十分な振動抑制効果を得ることができないという課題があった。   As described above, conventionally, the orifice diameter has been reduced as a means for further increasing the static rigidity (about φ2.0 mm or less). However, if 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.

そこで本発明では、オリフィス径を小さくし過ぎることなく、ミル振動を抑制することができる、圧延機を提供することを目的とする。   Accordingly, an object of the present invention is to provide a rolling mill that can suppress mill vibration without excessively reducing the orifice diameter.

上記課題を解決する第１の発明に係る圧延機は、
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。The rolling mill according to the first invention for solving the above-mentioned problems is as follows.
A housing;
A pair of upper and lower work roll chocks supported by the housing;
A pair of upper and lower work rolls that are pivotally supported by the pair of upper and lower work roll chocks and that face each other,
A reduction means for applying a predetermined pressure to the work roll;
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;
Using 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 part is φ2.5 mm or more and is 15% to 85% of the inner diameter of the hydraulic supply / discharge pipe.

上記課題を解決する第２の発明に係る圧延機は、
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。A rolling mill according to a second invention that solves the above problems is as follows.
In the rolling mill according to the first invention,
The volume of the enlarged portion is 7% to 180% with respect to the volume of the hydraulic pressing means.

上記課題を解決する第３の発明に係る圧延機は、
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。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.

上記課題を解決する第４の発明に係る圧延機は、
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。A rolling mill according to a fourth invention for solving the above-mentioned problem is as follows.
In the rolling mill according to any one of the first to third aspects,
The distance between the enlarged portion and the contracted portion in the hydraulic supply / discharge pipe is 3.5 m or less.

本発明に係る圧延機によれば、オリフィス径を小さくし過ぎることなく、ミル振動を抑制することができる。   According to the rolling mill according to the present invention, mill vibration can be suppressed without making the orifice diameter too small.

本発明の実施例１に係る圧延機の概略図である。It is the schematic of the rolling mill which concerns on Example 1 of this invention. 従来の圧延機の、オリフィス径と、静剛性、減衰比、動剛性との関係をそれぞれ示すグラフである。It is a graph which shows the relationship between the orifice diameter of a conventional rolling mill, static rigidity, a damping ratio, and dynamic rigidity, respectively. 本発明の実施例１に係る圧延機の、オリフィス径と、静剛性、減衰比、動剛性との関係をそれぞれ示すグラフである。It is a graph which shows the relationship between the orifice diameter of each rolling mill which concerns on Example 1 of this invention, a static rigidity, a damping ratio, and dynamic rigidity, respectively. 本発明の実施例１に係る圧延機の、動剛性に関する解析モデル図である。It is an analysis model figure about dynamic rigidity of a rolling mill concerning Example 1 of the present invention. 本発明の実施例１に係る圧延機の、加振力及びワークロール変位を示すグラフである。It is a graph which shows the exciting force and work roll displacement of the rolling mill which concerns on Example 1 of this invention. 本発明の実施例１に係る圧延機の、加振周波数と動剛性との関係を示すグラフである。It is a graph which shows the relationship between an excitation frequency and dynamic rigidity of the rolling mill which concerns on Example 1 of this invention. 本発明の実施例１に係る圧延機の、オリフィス径と動剛性比との関係を示すグラフである。It is a graph which shows the relationship between the orifice diameter and dynamic rigidity ratio of the rolling mill which concerns on Example 1 of this invention. 本発明の実施例１に係る圧延機の、チャンバ体積と動剛性比との関係を示すグラフである。It is a graph which shows the relationship between the chamber volume and dynamic rigidity ratio of the rolling mill which concerns on Example 1 of this invention. 本発明の実施例１に係る圧延機の、シリンダ‐オリフィス間距離と、動剛性比との関係を示すグラフである。It is a graph which shows the relationship between the distance between cylinder-orifices, and dynamic rigidity ratio of the rolling mill which concerns on Example 1 of this invention. 本発明の実施例１に係る圧延機の、オリフィス‐チャンバ間距離と、動剛性比との関係を示すグラフである。It is a graph which shows the relationship between the distance between orifice-chambers, and dynamic rigidity ratio of the rolling mill which concerns on Example 1 of this invention.

本発明に係る圧延機は、発明者の鋭意検討により、適正なチャンバを設けることにより、減衰比がオリフィス径により変化する特性を見出し、静剛性及び減衰比から求められる動剛性に着目したところ、ミル振動抑制の観点からオリフィス径に適正な範囲があることを見出したものである。また、チャンバ容量においても、適正な範囲があることも見出したものである。以下、本発明に係る圧延機について、実施例にて図面を用いて説明する。   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. Hereinafter, the rolling mill according to the present invention will be described with reference to the drawings in Examples.

［実施例１］
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。[Example 1]
First, a rolling mill according to Embodiment 1 of the present invention will be described with reference to FIG. FIG. 1 is a schematic view of a rolling mill according to Embodiment 1 of the present invention.

本発明の実施例１に係る圧延機は、図１（ａ）に示すように、ハウジング１１、ワークロール１２、ワークロールチョック１３、バックアップロール１４、バックアップロールチョック１５、圧下手段１６、油圧シリンダ１７（油圧式押圧手段、第１支持手段）、ハウジングライナ１８（第２支持手段）、油圧給排管１９、オリフィス２０（縮流部）、チャンバ２１（拡大部）、及び、油圧源２２を備える。   As shown in FIG. 1A, the rolling mill according to the first embodiment of the present invention 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.

上下一対のワークロールチョック１３は、ハウジング１１に支持されている。   A pair of upper and lower work roll chocks 13 are supported by the housing 11.

上下一対のワークロール１２は、互いに対向しており、上下一対のワークロールチョック１３にそれぞれ軸支されている。   The pair of upper and lower work rolls 12 are opposed to each other and are pivotally supported by a pair of upper and lower work roll chock 13 respectively.

上下一対のバックアップロール１４は、上下一対のバックアップロールチョック１５にそれぞれ軸支されており、上下一対のワークロール１２にそれぞれ対向している。   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.

圧下手段１６は、バックアップロール１４を介して、ワークロール１２に所定圧力を作用させている。   The reduction means 16 applies a predetermined pressure to the work roll 12 via the backup roll 14.

上下一対の油圧シリンダ１７は、ハウジング１１における圧延方向一方に設けられて上下一対のワークロールチョック１３を支持し、かつ、上下一対のワークロールチョック１３を水平方向に押圧可能とする。   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.

上下一対のハウジングライナ１８は、ハウジング１１における圧延方向他方に設けられて上下一対のワークロールチョック１３を支持している。   The pair of upper and lower housing liners 18 are provided on the other side of the housing 11 in the rolling direction and support the pair of upper and lower work roll chocks 13.

オリフィス２０及びチャンバ２１は、油圧シリンダ１７のヘッド側の油圧給排管１９に、オリフィス２０がチャンバ２１よりも油圧シリンダ１７側に配置されるように、設けられている。また、本発明の実施例１に係る圧延機は、図１（ｂ）のように、油圧給排管１９から配管を分岐させてチャンバ２１を配置してもよい。   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. Moreover, the rolling mill which concerns on Example 1 of this invention may branch piping from the hydraulic supply / exhaust pipe 19 and may arrange | position the chamber 21 like FIG.1 (b).

以下、オリフィス径（オリフィス２０の内径）について説明する。   Hereinafter, the orifice diameter (the inner diameter of the orifice 20) will be described.

本発明の実施例１に係る圧延機は、ミル振動の抑制として、圧延機の水平方向の動剛性を上げることに着目したものである。この動剛性（Ｋd）は、２×静剛性（Ｋ）×減衰比（ζ）にて表される。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 (ζ).

図２は、従来の圧延機の、静剛性、減衰比、動剛性と、オリフィス径との関係をそれぞれ示すグラフである。図３は、本発明の実施例１に係る圧延機の、静剛性、減衰比、動剛性と、オリフィス径との関係をそれぞれ示すグラフである。図２（ａ）及び図３（ａ）は、静剛性とオリフィス径との関係を示すグラフである。図２（ｂ）及び図３（ｂ）は、減衰比とオリフィス径との関係を示すグラフである。図２（ｃ）及び図３（ｃ）は、動剛性とオリフィス径との関係を示すグラフである。   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.

図２（ａ）（ｂ）に示すように、従来は、オリフィス径によらず、減衰比は、一定との概念より、静剛性及び動剛性は、オリフィス径を小さくするほど大きくなると考えていた。しかし、発明者の鋭意検討により、図３（ｂ）に示すように適正なチャンバを設けることにより、減衰比がオリフィス径により変化する特性を見出した。   As shown in FIGS. 2 (a) and 2 (b), conventionally, it was considered that the static stiffness and the dynamic stiffness become larger as the orifice diameter is smaller than the concept that the damping ratio is constant regardless of the orifice diameter. . However, as a result of intensive studies by the inventors, it has been found that the damping ratio varies depending on the orifice diameter by providing an appropriate chamber as shown in FIG.

つまり、図３（ａ）（ｂ）に示すように、オリフィス径を小さくすると、静剛性は大きくなるが、油圧給排管１９内の油がオリフィス２０を流れにくくなり減衰比は小さくなる。一方、オリフィス径を大きくすると、静剛性は下がるが、油圧給排管１９内の油がオリフィス２０を流れやすくなり、減衰比は上がる。   That is, as shown in FIGS. 3A and 3B, when the orifice diameter is reduced, the static rigidity is increased, but the oil in the hydraulic supply / discharge pipe 19 is less likely to flow through the orifice 20 and the attenuation ratio is reduced. On the other hand, when the orifice diameter is increased, the static rigidity is lowered, but the oil in the hydraulic supply / discharge pipe 19 easily flows through the orifice 20 and the damping ratio is increased.

そして、図３（ｃ）に示すように、所定の範囲のオリフィス径（後述）に設定すると、動剛性が特に向上することがわかった。   And as shown in FIG.3 (c), when it set to the orifice diameter (after-mentioned) of a predetermined range, it turned out that dynamic rigidity improves especially.

ただし、従来は、油圧給排管１９にオリフィス２０のみを設けた状態では、図２（ａ）（ｂ）に示すように、オリフィス径を拡大しても減衰比は一定となるとの概念により、静剛性のみに着目し、オリフィス径を小さく（約φ２．０ｍｍ又はそれ以下）していた。   However, conventionally, in the state where only the orifice 20 is provided in the hydraulic supply / discharge pipe 19, as shown in FIGS. 2A and 2B, the damping ratio is constant even if the orifice diameter is enlarged, Focusing only on static rigidity, the orifice diameter was reduced (about φ2.0 mm or less).

しかし、チャンバ２１を設置することで、上述のようにオリフィス径を拡大すると減衰比が向上することがわかった。よって、本実施例では、チャンバ２１を設けた上で、オリフィス径と減衰比、すなわち動剛性に着目し、より振動抑制効果を増大できるオリフィス径の適正な範囲を見出したものである。   However, it has been found that by installing the chamber 21, the damping ratio is improved when the orifice diameter is enlarged 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.

また、油圧シリンダ１７からバルブスタンドまで距離があり、さらにオリフィス２０により径が絞られているため、オリフィス２０だけを設けたとしても、油圧給排管１９内の油が流れにくい状況となり、減衰比が上がらなくなる。   In addition, since there is a distance from the hydraulic cylinder 17 to the valve stand and the diameter is restricted by the orifice 20, even if only the orifice 20 is provided, the oil in the hydraulic supply / discharge pipe 19 is difficult to flow, and the damping ratio Will not rise.

しかし、本発明の実施例１に係る圧延機では、油圧給排管１９において、チャンバをオリフィス２０の出側に設置していることで、圧力差を発生させ、オリフィス２０に油を流すことで、減衰比を向上することができる。   However, in the rolling mill according to the first embodiment of the present invention, 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.

また、チャンバ２１においても、動剛性の観点から、所定の範囲の容量（後述）に設定すると、動剛性が特に向上することが見出された。   In the chamber 21 as well, from the viewpoint of dynamic rigidity, it was found that the dynamic rigidity is particularly improved when the capacity is set within a predetermined range (described later).

以下、動剛性が特に向上するオリフィス径の範囲を求める。   Hereinafter, the range of the orifice diameter in which the dynamic rigidity is particularly improved is obtained.

図４は、動剛性のシミュレーションモデル図である。図４中のＡはオリフィス２０、Ｂは油圧給排管１９、Ｋ１はハウジングのばね定数、Ｋはモデル全体における静剛性、ｃは構造物の減衰係数、Ｄはハウジング１１、Ｅはワークロール１２とワークロールチョック１３、Ｆは油圧シリンダ１７、Ｐは油圧ポンプを、それぞれモデル化したものである。ワークロール１２とワークロールチョック１３の運動方程式、そして、オリフィス２０には圧力差で流量が決まる特性を組み入れた。   FIG. 4 is a simulation model diagram of dynamic stiffness. 4, 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, and E is the work roll 12. The work roll chock 13, F is a hydraulic cylinder 17, and 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.

図４より、運動方程式は下記式（１）（２）で表される。   From FIG. 4, the equation of motion is expressed by the following equations (1) and (2).

Figure 0006345262
Figure 0006345262

Figure 0006345262
Figure 0006345262

さらに、動剛性Ｋdは下記式（３）で表される。Furthermore, the dynamic stiffness Kd is expressed by the following formula (3).

Figure 0006345262
Figure 0006345262

上記式（１）より、加振力ｆ0とワークロール変位Ｘとの関係は、図５のグラフに示すようになる。From the above equation (1), the relationship between the excitation force f 0 and the work roll displacement X is as shown in the graph of FIG.

そして、加振周波数ωごとのワークロール変位Ｘを計算し、加振力ｆ0とワークロール変位Ｘとの比を算出（上記式（３））する。ただし、この比の値は、図６に示すように加振周波数ωの値により変化する。Then, the work roll displacement X for each excitation frequency ω is calculated, and the ratio between the excitation force f 0 and the work roll displacement X is calculated (the above formula (3)). However, the value of this ratio varies depending on the value of the excitation frequency ω as shown in FIG.

そこで、加振周波数ωの値により変化する加振力ｆ0とワークロール変位Ｘとの比の中の最小値を、動剛性Ｋdとして求める。すなわち、動剛性Ｋdは、加振周波数ωごとに加振力ｆ0を与え、加振力ｆ0とワークロール変位Ｘとの比の最小値として表され、振動時の動きを決める値となる。Therefore, the minimum value in the ratio between the excitation force f 0 and the work roll displacement X that varies depending on the value of the excitation frequency ω is obtained as the dynamic stiffness K d . That is, the dynamic stiffness K d gives an excitation force f 0 for each excitation frequency ω, 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. Become.

上述のようにしてオリフィス径ごとに動剛性Ｋdを求めたところ、図７（ａ）（ｂ）に示す結果となった。When the dynamic rigidity Kd was obtained for each orifice diameter as described above, the results shown in FIGS. 7A and 7B were obtained.

図７（ａ）は、オリフィス径と動剛性比との関係を示すグラフであり、図７（ｂ）は、オリフィス径の油圧給排管１９内径に対する比（オリフィス径の配管内径比）と、動剛性比との関係を示すグラフである。なお、図７（ａ）は、油圧給排管１９の内径（配管内径）がφ１８ｍｍの場合である。また、動剛性比とは、オリフィス径が０、すなわち油圧シリンダ封じきり状態の場合の動剛性に対する比を指す（図８〜９も同様）。   FIG. 7A is a graph showing the relationship between the orifice diameter and the dynamic stiffness ratio, and 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 φ18 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).

図７（ａ）（ｂ）に示すように、従来は約φ２．０ｍｍ以下に設計していたオリフィス径を、逆に大きく設計することで、動剛性比がより向上することを見出した。特に、図７（ａ）では、オリフィス径２．５ｍｍ及び１５ｍｍに変曲点を有し、２．５ｍｍ以上１５ｍｍ以下では、動剛性比が急上昇しており、図７（ｂ）では、オリフィス径の配管内径比が０．１５（１５％）及び０．８５（８５％）に変曲点を有し、１５％以上８５％以下では、動剛性比が急上昇している。   As shown in FIGS. 7 (a) and 7 (b), it has been found that the dynamic stiffness ratio is further improved by designing the orifice diameter, which was conventionally designed to be about φ2.0 mm or less, on the contrary. In particular, in FIG. 7 (a), 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. In FIG. 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.

また、オリフィス径φ２．５ｍｍ以上とすれば、従来の問題点であったゴミ詰まりも発生し難くなる。   In addition, if the orifice diameter is 2.5 mm or more, dust clogging, which has been a conventional problem, is less likely to occur.

したがって、本発明の実施例１に係る圧延機では、オリフィス径を、φ２．５ｍｍ以上、かつ、配管内径比１５％〜８５％の大きさとする。なお、このとき、動剛性比は１．２以上に向上する。   Therefore, in the rolling mill according to Example 1 of the present invention, the orifice diameter is set to φ2.5 mm or more and the pipe inner diameter ratio is 15% to 85%. At this time, the dynamic stiffness ratio is improved to 1.2 or more.

また、チャンバ２１の容量についても、動剛性比との関係を求めた結果、図８（ａ）（ｂ）に示すようになることを見出した。   Also, as a result of obtaining the relationship between the capacity of the chamber 21 and the dynamic rigidity ratio, it has been found that the capacity is as shown in FIGS.

図８（ａ）は、チャンバ２１の容量（チャンバ体積）と動剛性比との関係を示すグラフであり、図８（ｂ）は、チャンバ体積の油圧シリンダ１７体積に対する比（チャンバ体積のシリンダ体積比）と、動剛性比との関係を示すグラフである。   FIG. 8A is a graph showing the relationship between the capacity of the chamber 21 (chamber volume) and the dynamic stiffness ratio, and 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.

ここで、シリンダ体積とは、シリンダ径とストロークで決まる容量で定義した。具体例としては、油圧シリンダサイズがＤ２５０ｍｍ（ヘッド径）／ｄ２３０ｍｍ（ロッド径）×９０ｍｍストロークの場合、シリンダ体積Ｖｃ＝（π／４）×２５2×９（ｃｍ3）となり、約４．４リットルとなる。したがって、後述の如く、チャンバ体積が０．３リットル〜８．０リットルでは、チャンバ体積のシリンダ体積比が０．０７〜１．８となる。Here, the cylinder volume was defined by the capacity determined by the cylinder diameter and stroke. As a specific example, when the hydraulic cylinder size is D250 mm (head diameter) / d230 mm (rod diameter) × 90 mm stroke, the cylinder volume Vc = (π / 4) × 25 2 × 9 (cm 3 ), which is about 4.4. Liters. Therefore, as will be described later, when 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.

図８（ａ）に示すように、チャンバ体積０．３リットル以上で、動剛性比が１．２以上、最大３．０程度まで向上する。すなわち、図８（ｂ）に示すように、チャンバ体積のシリンダ体積比０．０７以上で、動剛性比が１．２以上、最大３．０程度まで向上する。   As shown in FIG. 8A, when the chamber volume is 0.3 liters or more, the dynamic stiffness ratio is improved to 1.2 or more and up to 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.

なお、図８（ａ）におけるチャンバ体積が８．０リットルより大きい値、すなわち、図８（ｂ）におけるチャンバ体積のシリンダ体積比が１．８より大きい値については、グラフが飽和状態となり、動剛性比は殆ど向上しなくなるため、それ以上チャンバ体積を大きくしても大幅な効果の増大にはならないことを見出した。   For the value of the chamber volume in FIG. 8 (a) larger than 8.0 liters, that is, the value of the chamber volume cylinder volume ratio in FIG. Since the stiffness ratio is hardly improved, it has been found that increasing the chamber volume beyond that does not significantly increase the effect.

したがって、本発明の実施例１に係る圧延機では、チャンバ体積のシリンダ体積比を、０．０７以上１．８以下（すなわち、７％以上１８０％以下）とする。なお、このとき、動剛性比は１．２以上となる。   Therefore, in the rolling mill according to Example 1 of the present invention, 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.

また、油圧シリンダ１７とオリフィス２０との間の距離（シリンダ‐オリフィス間距離）についても動剛性比との関係について追究した結果、図９のグラフに示すように、シリンダ‐オリフィス間距離が７．０ｍ以下であると、動剛性比は１．２以上となることを見出した。   Further, as a result of investigating the relationship between the dynamic rigidity ratio and the distance between the hydraulic cylinder 17 and the orifice 20 (cylinder-orifice distance), as shown in the graph of FIG. It has been found that the dynamic rigidity ratio is 1.2 or more when it is 0 m or less.

したがって、本発明の実施例１に係る圧延機では、シリンダ‐オリフィス間距離を７．０ｍ以下とする。   Therefore, in the rolling mill according to Example 1 of the present invention, the distance between the cylinder and the orifice is set to 7.0 m or less.

さらに、オリフィス２０とチャンバ２１との間の距離（オリフィス‐チャンバ間距離）についても動剛性比との関係についても追究した結果、図１０のグラフに示すように、オリフィス‐チャンバ間距離が３．５ｍ以下であると、動剛性比は１．２以上となることを見出した。   Furthermore, as a result of investigating the relationship between the distance between the orifice 20 and the chamber 21 (orifice-chamber distance) and the dynamic stiffness ratio, as shown in the graph of FIG. It has been found that the dynamic rigidity ratio is 1.2 or more when it is 5 m or less.

したがって、本発明の実施例１に係る圧延機では、オリフィス‐チャンバ間距離を３．５ｍ以下とする。   Therefore, in the rolling mill according to Example 1 of the present invention, the distance between the orifice and the chamber is set to 3.5 m or less.

以上、本発明の実施例１に係る圧延機について説明した。本発明の実施例１に係る圧延機は、図１，２においてはオリフィス２０及びチャンバ２１を油圧給排管１９のヘッド側のみに設けるようにしたが、さらにロッド側にもオリフィス及びチャンバを設けてもよい。また、油圧給排管１９ロッド側には、オリフィスのみを設けてチャンバは設けないようにしてもよい。いずれにしてもオリフィス２０及びチャンバ２１の効果は変わらない。   The rolling mill according to the first embodiment of the present invention has been described above. In the rolling mill according to Embodiment 1 of the present invention, 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.

本発明の実施例１に係る圧延機は、上述の構成とすることで、オリフィス径を小さくし過ぎることなく、ミル振動を抑制することができるものである。   The rolling mill according to the first embodiment of the present invention can suppress mill vibration without reducing the orifice diameter by using the above-described configuration.

本発明は、圧延機、特に熱間圧延機の圧延中に発生する圧延機の振動を抑制する装置として好適である。   The present invention is suitable as a device for suppressing vibration of a rolling mill, particularly a rolling mill generated during rolling of a hot rolling mill.

１１ ハウジング
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DESCRIPTION OF SYMBOLS 11 Housing 12 Work roll 13 Work roll chock 14 Backup roll 15 Backup roll chock 16 Reduction means 17 Hydraulic cylinder 18 Housing liner 19 Hydraulic supply / discharge pipe 20 Orifice 21 Chamber 22 Hydraulic source

Claims (3)

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％の大きさとし、
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％以上とし、
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以下とし、
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
ことを特徴とする圧延機。 A housing;
A pair of upper and lower work roll chocks supported by the housing;
A pair of upper and lower work rolls that are pivotally supported by the pair of upper and lower work roll chocks and that face each other,
A reduction means for applying a predetermined pressure to the work roll;
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;
Using 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 contraction portion, or 2.5 mm, and a size of 15% to 85% with respect to the inner diameter of the hydraulic supply and discharge line,
The volume of the enlarged portion is 7% or more with respect to the volume of the hydraulic pressing means,
The 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 , wherein an interval between the enlarged portion and the contracted portion in the hydraulic supply / discharge pipe is 3.5 m or less . 前記拡大部の体積を前記油圧式押圧手段の体積に対し１８０％以下とする
ことを特徴とする、請求項１に記載の圧延機。 Wherein the volume of the enlarged portion, characterized in that the following 1 80% against the volume of the hydraulic pushing means, the rolling mill of claim 1. ハウジングと、  A housing;
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、  A pair of upper and lower work roll chocks supported by the housing;
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、  A pair of upper and lower work rolls that are pivotally supported by the pair of upper and lower work roll chocks and that face each other,
前記ワークロールに所定圧力を作用させる圧下手段と、  A reduction means for applying a predetermined pressure to the work roll;
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、  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;
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、  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;
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、  Using 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,
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  The inner diameter of the contracted flow portion is φ2.5 mm or more and a size of 15% to 85% with respect to the inner diameter of the hydraulic supply / discharge pipe.
圧延機であって、A rolling mill,
前記圧延機において前記縮流部の内径がゼロであると仮定したときの動剛性に対する前記圧延機の動剛性の比である動剛性比が１．２以上である  In the rolling mill, the dynamic stiffness ratio, which is the ratio of the dynamic stiffness of the rolling mill to the dynamic stiffness when assuming that the inner diameter of the reduced flow portion is zero, is 1.2 or more.
ことを特徴とする圧延機。A rolling mill characterized by that.
JP2016552761A 2014-10-09 2014-10-09 Rolling mill Active JP6345262B2 (en)

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JPS61259810A (en) * 1985-05-10 1986-11-18 Ishikawajima Harima Heavy Ind Co Ltd Method and apparatus for rolling
JPH02151310A (en) * 1988-12-05 1990-06-11 Sumitomo Light Metal Ind Ltd Vibration isolator in rolling mill
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