JP4341103B2 - Oil film bearing - Google Patents

Oil film bearing Download PDF

Info

Publication number
JP4341103B2
JP4341103B2 JP07131099A JP7131099A JP4341103B2 JP 4341103 B2 JP4341103 B2 JP 4341103B2 JP 07131099 A JP07131099 A JP 07131099A JP 7131099 A JP7131099 A JP 7131099A JP 4341103 B2 JP4341103 B2 JP 4341103B2
Authority
JP
Japan
Prior art keywords
oil
roll
bushing
pad
sleeve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
JP07131099A
Other languages
Japanese (ja)
Other versions
JP2000263108A (en
Inventor
幸平 竹沢
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
JFE Steel Corp
Original Assignee
JFE Steel Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by JFE Steel Corp filed Critical JFE Steel Corp
Priority to JP07131099A priority Critical patent/JP4341103B2/en
Publication of JP2000263108A publication Critical patent/JP2000263108A/en
Application granted granted Critical
Publication of JP4341103B2 publication Critical patent/JP4341103B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

Classifications

    • 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
    • B21B31/07—Adaptation of roll neck bearings
    • B21B31/076—Cooling; Lubricating roller bearings
    • 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
    • B21B31/07—Adaptation of roll neck bearings
    • B21B31/074—Oil film bearings, e.g. "Morgoil" bearings

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Sliding-Contact Bearings (AREA)

Description

【０００１】
【発明の属する技術分野】
本発明は、ロールの油膜軸受に関するもので、特に圧延機の補強ロールに用いて好適な油膜軸受に関する。
【０００２】
【従来の技術】
被圧延材の圧延反力を受ける一対の補強ロール１は、図３に示すように、一対の作業ロール11の上下に設けられるとともに、油膜軸受の軸受箱３を介して、回動自在にハウジング12に支持されている。その補強ロール１の油膜軸受は、上側の補強ロール１の左右の２個所および下側の補強ロールの左右の２個所の合計４個所に用いられている。なお、Ｓは被圧延材である。
【０００３】
下側の補強ロールの油膜軸受のロール軸方向断面図を図４に、図４のＸ−Ｘ断面図を図５に示す。
従来の補強ロール１の油膜軸受は、軸受箱３と、軸受箱３の内部に装着された円筒状のブッシング４と、補強ロール１のロールネック部10の外周に装着されたスリーブ２とを備え、ブッシングの内部にスリーブを装着している。そして、スリーブ２の外面とブッシング４の内面の隙間に潤滑油を供給し、補強ロール１が回転するとスリーブ２の外面とブッシング４の内面との隙間に潤滑油の油膜が形成されるので、補強ロール１のロールネック部10はスリーブ２を介してブッシング４の内面に接触することなく回転支持されるのである。
【０００４】
しかし、補強ロールの回転数が低い圧延開始時や低速圧延時、あるいは高荷重圧延時では、スリーブ２の外面とブッシング４の内面間の下部隙間が小さくなって油膜が破断し、スリーブ２の外面とブッシング４の内面の下部で焼付きが発生しやすい。
そこで、この焼付きを防止するために、荷重の作用する方向のブッシング４の下部内面にオイルパッド５（凹み）を設け、オイルパッド５に高圧（約700kgf/cm2) の潤滑油を供給するハイドロスタティック潤滑装置が油膜軸受に備えられている。このオイルパッド５は、上側の補強ロールの油膜軸受では、荷重が上方に作用するのでブッシング４の上部内面に設けられている。また、このような油膜軸受は２重式の高速高荷重の作業ロールにも適用されている。
【０００５】
【発明が解決しようとする課題】
ところが、ロールの回転を停止（圧延を停止）した際に、ロールの軸芯がブッシング４の中心を通る垂直線からずれていることがあるために、前記ハイドロスタティック潤滑装置からの高圧油が有効に作用せずロールを回転した時にスリーブの外面とブッシングの内面とが焼きつくという問題があった。
【０００６】
特に、１パスの圧延毎に正転と逆転を繰り返すリバース圧延に、油膜軸受を用いるとスリーブの外面とブッシングの内面とが焼きつく頻度が多くなるという問題があった。
そこで、本発明の目的は、従来技術の上記問題点を解消することにあり、ロールの停止位置によらず、ロールを回転した時にスリーブとブッシングとの焼付きが発生しない油膜軸受を提供することにある。
【０００７】
【課題を解決するための手段】
本発明は、軸受箱と、該軸受箱に内装された円筒状のブッシングと、ロールのロールネック部に外装されたスリーブとを備え、前記ブッシングの内部に前記スリーブを装着して、前記ブッシングの内面と前記スリーブの外面との隙間に潤滑油の油膜を形成する油膜軸受であって、前記ロールが回動自在にハウジングに支持された状態で、前記ロールの回転を開始する始動時には、オイルパッド（凹み）に前記ロールを浮上させ得る圧力で潤滑油を供給し、前記ロールの回転数が所定となったときには、オイルパッドに潤滑油を供給するのを停止し、別のノズルから前記ロールを浮上させ得る圧力よりも低圧で潤滑油を供給して前記隙間に潤滑油の油膜を形成するように構成され、前記ブッシングの荷重が作用する方向の上部内面または下部内面のロール軸方向中央部に、少なくとも一つのオイルパッドを設け、該オイルパッドには前記ロールを浮上させ得る高圧の潤滑油を供給するハイドロスタティック潤滑装置が接続され、それに加えてさらに、前記ブッシングの内面の荷重が作用する方向のオイルパッドを挟む円周方向の両側に、対称に前記ブッシングの中心と荷重が作用する方向のオイルパッドの円周方向中央とを結ぶ仮想線に対する中心角が45〜90°となる位置に円周方向中央が位置するようにそれぞれ少なくとも一つのオイルパッドを設け、前記ロールの回転を開始する始動時に、前記ブッシングの内面に設けられた荷重が作用する方向のオイルパッド及び該オイルパッドを挟んで円周方向両側に対称に設けたオイルパッドに前記ロールを浮上させ得る高圧の潤滑油を供給し、前記ロールを浮上させるようにしたことを特徴とする油膜軸受である。
【０００８】
【発明の実施の形態】
本発明の油膜軸受を、４段圧延機の下側の補強ロールに用いた場合について、詳細に説明する。
本発明の油膜軸受に備えられた補強ロールのロールネック部の外周に装着されたスリーブは、図４、図５に示した従来の補強ロール１のロールネック部10の外周に装着されたスリーブ２と同じである。
【０００９】
本発明の油膜軸受の特徴は、図１および図２に示すように、補強ロール１のロールネック部10に外装されたスリーブ２と、軸受箱3aと、軸受箱3aの内部に装着された円筒状のブッシング4aを備え、ブッシング4aの内部にスリーブ２を装着していることである。図において、５、5a、5bはオイルパッド、６、6a、6b、７、7a、7bは油孔、８、8a、8bは給油口である。
【００１０】
オイルパッド５は、高圧の潤滑油が供給される凹みであって、荷重が作用する方向のブッシング4aの下部内面のロール軸方向中央部に少なくとも一つ設けられている。オイルパッド5 をブッシング4aの下部内面のロール軸方向中央部に少なくとも一つ設けた理由は、凹みに高圧の潤滑油を供給した時に、ブッシング4aの下部内面とスリーブ２の下部外面との隙間を増大する効果が大きく、ブッシング4aの下部内面とスリーブ２の下部外面との焼付きを効果的に防止できるからである。
【００１１】
また、油孔６、７は、軸受箱3aの端面からオイルパッド５に貫通する連通孔で、給油口８は、油孔７に設けられた潤滑油を供給する給油口である。オイルパッド５、油孔６、７および給油口８は、従来の油膜軸受に設けられているものと同じである。
オイルパッド5a、5bは、高圧の潤滑油が供給される凹みであって、ブッシング4aの内面のオイルパッド５を挟む円周方向の両側にそれぞれ少なくとも一つ設けられている。オイルパッド5a、5bを、ブッシング4aの内面のオイルパッド５を挟む円周方向の両側にそれぞれ少なくとも一つ設けた理由は、凹みに高圧の潤滑油を供給した時に、補強ロール１の軸芯をブッシング4aの中心を通る垂直線に合わせる効果が大きいからである。
【００１２】
このオイルパッド5a、5bの凹みの形状、寸法は、従来のオイルパッド５と同じにするのが好ましい。たとえば、ロールネック部直径600mm の補強ロールの油膜軸受では、ロール軸方向の長さ30〜50mm×周方向の長さ100 〜150mm ×最大深さ0.5 〜1.0mm 程度にするとよい。
またオイルパッド5a、5bは、ブッシング4aの内面のオイルパッド５を挟む円周方向の両側に、対称に設け、さらにオイルパッド5aおよび5bの円周方向中央と、オイルパッド５の円周方向中央と、ブッシング4aの中心とでなす中心角を、それぞれ45〜90°にするのが好ましく、90°にするのが最も好ましい。この理由は、ブッシング4aの下部内面とスリーブ２の下部外面との隙間を増大する効果があり、補強ロール１の軸芯をブッシング4aの中心を通る垂直線に合わせる効果が大きいからである。
【００１３】
油孔6a、7aは、軸受箱3aの端面からオイルパッド5aに貫通する連通孔であり、同様に油孔6b、7bは、軸受箱3aの端面からオイルパッド5bに貫通する連通孔である。また給油口8aは、油孔7aに設けられた潤滑油を供給する給油口であり、同様に給油口8bは、油孔7bに設けられた潤滑油を供給する給油口である。
そして、補強ロール１の回転を開始する始動時に、ブッシング4aの内面に設けられたオイルパッド５、5aおよび5bに高圧（約700kgf/cm2) の潤滑油を供給するようにしている。
【００１４】
本発明の油膜軸受の動作について、図２を用いて説明する。図２は、補強ロールを回転した時のブッシング4aのロール軸方向中央部におけるロール軸芯に直角な概略断面図である。
補強ロールの軸芯がブッシング4aの中心を通る垂直線の左側にずれて停止し、回転を開始する始動時に、ブッシング4aの内面とスリーブ２の外面とが左斜め下部で接触しているとして説明する。
【００１５】
本発明の油膜軸受では、補強ロールの回転を開始する始動時に、給油口から高圧の潤滑油を、油孔6 、7 を通して荷重が作用する下側のオイルパッド５に供給するととともに、別の給油口から同じ高圧の潤滑油を、油孔6a、7aを通して右側のオイルパッド5aに供給し、さらに別の給油口から同じ高圧の潤滑油を、油孔6b、7bを通して左側のオイルパッド5bに供給する。
【００１６】
補強ロールの軸芯がブッシング４の中心を通る垂直線の左側にずれているので、左側のオイルパッド5bとスリーブ２の外面との間隔および下側のオイルパッド5 とスリーブ２の外面との間隔は、右側のオイルパッド5aとスリーブ２の外面との間隔よりも小さくなっている。その結果、補強ロールを浮上させる浮上力が、右斜め上方向に作用するので、補強ロールが右斜め上方向に浮上し、図２に示すように左斜め下部のブッシング4aの内面とスリーブ２の外面との間に隙間ができる。そこで、補強ロールを回転した時に、左斜め下部でのブッシング4aの内面とスリーブ２の外面との焼付きが防止できるのである。
【００１７】
その後、所定の補強ロールの回転数となったときには、オイルパッド５およびオイルパッド5a、5bに高圧で潤滑油を供給するのを停止し、別のノズルから低圧で潤滑油を供給する。
一方、図４、図５に示す従来の油膜軸受では、補強ロール１の軸芯がブッシング４の中心を通る垂直線の左側にずれて停止し、回転を開始する始動時に、ブッシング４の内面とスリーブ２の外面とが左斜め下部で接触していると、荷重が作用する下側のオイルパッド５に供給された潤滑油は、補強ロール１を右斜め上方に浮上させることができない。その結果、補強ロールが回転した時にブッシング４の内面とスリーブ２の外面とが左斜め下部で焼きつくことになるのである。
【００１８】
以上の説明では、補強ロールの軸芯がブッシング4aの中心を通る垂直線の左側にずれて停止した場合に説明したが、補強ロールの軸芯がブッシング4aの中心を通る垂直線の右側にずれて停止した場合についても、本発明の油膜軸受では同様の原理によりスリーブ２の外面とブッシング4aの内面との焼付きが防止できる。また、下側の補強ロールに本発明の油膜軸受を用いた場合について説明したが、上側の補強ロールに本発明の、ブッシングの上部内面のロール軸方向中央部に少なくとも一つのオイルパッドを設け、それに加えてさらにブッシングの内面の前記オイルパッドを挟む円周方向の両側にそれぞれ少なくとも一つのオイルパッドを設けた油膜軸受を用いることにより、同様にしてスリーブの外面とブッシングの内面との焼付きが防止できる。
【００１９】
また、作業ロールに本発明の油膜軸受を用いることにより、同様にしてスリーブの外面とブッシングの内面との焼付きが防止できる。
【００２０】
【発明の効果】
本発明によれば、ロールの停止時にロールの軸芯がブッシングの中心を通る垂直線に一致していなくても、ロールを回転した時にスリーブの外面とブッシングの内面との焼付きが防止できる。
【図面の簡単な説明】
【図１】図１は本発明のブッシングを内装した軸受箱の概略斜視図である。
【図２】図２は本発明の油膜軸受の原理を説明する概略断面図である。
【図３】図３は油膜軸受を用いる４段圧延機の構成を示す概略正面図である。
【図４】図４は従来の油膜軸受のロール軸方向の概略断面図である。
【図５】図４のＸ−Ｘ概略断面図である。
【符号の説明】
１ 補強ロール
10 ロールネック部
２ スリーブ
３、3a 軸受箱
４、4a ブッシング
５、5a、5b オイルパッド
６、6a、6b 油孔
７、7a、7b 油孔
８、8a、8b 給油口[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an oil film bearing for a roll, and particularly to an oil film bearing suitable for use as a reinforcing roll of a rolling mill.
[0002]
[Prior art]
As shown in FIG. 3, the pair of reinforcing rolls 1 that receive the rolling reaction force of the material to be rolled are provided above and below the pair of work rolls 11, and are rotatably housed via the bearing housing 3 of the oil film bearing. Supported by 12. The oil film bearings of the reinforcing roll 1 are used in a total of four places, two on the left and right of the upper reinforcing roll 1 and two on the left and right of the lower reinforcing roll. S is a material to be rolled.
[0003]
FIG. 4 shows a sectional view in the roll axial direction of the oil film bearing of the lower reinforcing roll, and FIG. 5 shows an XX sectional view of FIG.
The oil film bearing of the conventional reinforcing roll 1 includes a bearing box 3, a cylindrical bushing 4 mounted inside the bearing box 3, and a sleeve 2 mounted on the outer periphery of the roll neck portion 10 of the reinforcing roll 1. The sleeve is mounted inside the bushing. Then, lubricating oil is supplied to the gap between the outer surface of the sleeve 2 and the inner surface of the bushing 4, and when the reinforcing roll 1 rotates, an oil film of lubricating oil is formed in the gap between the outer surface of the sleeve 2 and the inner surface of the bushing 4. The roll neck 10 of the roll 1 is rotatably supported without contacting the inner surface of the bushing 4 via the sleeve 2.
[0004]
However, at the start of rolling at a low rotation speed of the reinforcing roll, at the time of low speed rolling, or at the time of high load rolling, the lower gap between the outer surface of the sleeve 2 and the inner surface of the bushing 4 becomes small and the oil film breaks, and the outer surface of the sleeve 2 And seizure tends to occur at the lower part of the inner surface of the bushing 4.
Therefore, in order to prevent this seizure, an oil pad 5 (dent) is provided on the lower inner surface of the bushing 4 in the direction in which the load acts, and high-pressure (about 700 kgf / cm 2 ) lubricating oil is supplied to the oil pad 5. A hydrostatic lubrication device is provided in the oil film bearing. The oil pad 5 is provided on the upper inner surface of the bushing 4 because the load acts upward in the oil film bearing of the upper reinforcing roll. Such oil film bearings are also applied to double-type high-speed, high-load work rolls.
[0005]
[Problems to be solved by the invention]
However, when the roll rotation is stopped (rolling is stopped), the roll axis may be displaced from the vertical line passing through the center of the bushing 4, so the high pressure oil from the hydrostatic lubrication device is effective. There was a problem that the outer surface of the sleeve and the inner surface of the bushing burned when the roll was rotated without acting on the surface.
[0006]
In particular, when an oil film bearing is used for reverse rolling that repeats forward rotation and reverse rotation every rolling of one pass, there has been a problem that the outer surface of the sleeve and the inner surface of the bushing are burned more frequently.
Accordingly, an object of the present invention is to eliminate the above-mentioned problems of the prior art, and to provide an oil film bearing in which seizure between the sleeve and the bushing does not occur when the roll is rotated regardless of the stop position of the roll. It is in.
[0007]
[Means for Solving the Problems]
The present invention comprises a bearing box, a cylindrical bushing that is housed in the bearing box, and a sleeve that is externally mounted on a roll neck portion of a roll. An oil film bearing for forming an oil film of lubricating oil in a gap between an inner surface and the outer surface of the sleeve, wherein the oil pad is started at the start of rotation of the roll while the roll is rotatably supported by a housing. Lubricating oil is supplied at a pressure that allows the roll to float (indent), and when the rotation speed of the roll reaches a predetermined value, the supply of lubricating oil to the oil pad is stopped, and the roll is removed from another nozzle. The lubricating oil is supplied at a pressure lower than the pressure that can be levitated to form an oil film of the lubricating oil in the gap, and in the upper inner surface or the lower portion in the direction in which the load of the bushing acts To the roll axis direction central portion, at least one of the oil pad provided in the oil pad connected hydrostatic lubrication device supplies lubricating oil of the high pressure capable of floating the roll, in addition to that, of the bushing A central angle with respect to an imaginary line connecting the center of the bushing and the circumferential center of the oil pad in the direction in which the load acts symmetrically on both sides in the circumferential direction across the oil pad in the direction in which the load on the inner surface acts is 45 to At least one oil pad is provided so that the center in the circumferential direction is positioned at 90 °, and the oil pad in the direction in which the load provided on the inner surface of the bushing acts at the start of rotation of the roll and supplying high-pressure lubricating oil capable of floating the roll oil pad provided symmetrically in the circumferential direction both sides of the oil pad A oil film bearing which is characterized in that so as to float the roll.
[0008]
DETAILED DESCRIPTION OF THE INVENTION
The case where the oil film bearing of the present invention is used for the lower reinforcing roll of the four-high rolling mill will be described in detail.
The sleeve mounted on the outer periphery of the roll neck portion of the reinforcing roll provided in the oil film bearing of the present invention is the sleeve 2 mounted on the outer periphery of the roll neck portion 10 of the conventional reinforcing roll 1 shown in FIGS. Is the same.
[0009]
As shown in FIGS. 1 and 2, the oil film bearing according to the present invention is characterized by a sleeve 2 sheathed on a roll neck portion 10 of a reinforcing roll 1, a bearing box 3a, and a cylinder mounted inside the bearing box 3a. In other words, the bushing 4a is provided and the sleeve 2 is mounted inside the bushing 4a. In the figure, 5, 5a, 5b are oil pads, 6, 6a, 6b, 7, 7a, 7b are oil holes, and 8, 8a, 8b are oil supply ports.
[0010]
The oil pad 5 is a recess to which high-pressure lubricating oil is supplied, and is provided at least one at the center in the roll axial direction of the lower inner surface of the bushing 4a in the direction in which the load acts. The reason why at least one oil pad 5 is provided in the central portion in the roll axial direction of the lower inner surface of the bushing 4a is that when a high-pressure lubricating oil is supplied to the recess, a gap is formed between the lower inner surface of the bushing 4a and the lower outer surface of the sleeve 2. This is because the effect of increasing is great and seizure between the lower inner surface of the bushing 4a and the lower outer surface of the sleeve 2 can be effectively prevented.
[0011]
The oil holes 6 and 7 are communication holes that penetrate from the end face of the bearing housing 3 a to the oil pad 5, and the oil supply port 8 is an oil supply port that supplies lubricating oil provided in the oil hole 7. The oil pad 5, the oil holes 6, 7 and the oil supply port 8 are the same as those provided in the conventional oil film bearing.
The oil pads 5a and 5b are depressions to which high-pressure lubricating oil is supplied, and at least one is provided on each of both sides in the circumferential direction sandwiching the oil pad 5 on the inner surface of the bushing 4a. The reason why at least one oil pad 5a, 5b is provided on both sides in the circumferential direction sandwiching the oil pad 5 on the inner surface of the bushing 4a is that when the high pressure lubricating oil is supplied to the recess, the shaft core of the reinforcing roll 1 is provided. This is because the effect of matching the vertical line passing through the center of the bushing 4a is great.
[0012]
The shape and dimensions of the recesses of the oil pads 5a and 5b are preferably the same as those of the conventional oil pad 5. For example, in an oil film bearing of a reinforced roll having a roll neck portion diameter of 600 mm, the length in the roll axis direction is 30 to 50 mm × the length in the circumferential direction is 100 to 150 mm × the maximum depth is about 0.5 to 1.0 mm.
The oil pads 5a and 5b are provided symmetrically on both sides in the circumferential direction sandwiching the oil pad 5 on the inner surface of the bushing 4a. Further, the circumferential center of the oil pads 5a and 5b and the circumferential center of the oil pad 5 are provided. And the center angle formed by the center of the bushing 4a is preferably 45 to 90 °, and most preferably 90 °. This is because there is an effect of increasing the gap between the lower inner surface of the bushing 4a and the lower outer surface of the sleeve 2, and the effect of aligning the axis of the reinforcing roll 1 with a vertical line passing through the center of the bushing 4a is great.
[0013]
The oil holes 6a and 7a are communication holes that penetrate from the end face of the bearing box 3a to the oil pad 5a. Similarly, the oil holes 6b and 7b are communication holes that penetrate from the end face of the bearing box 3a to the oil pad 5b. The oil supply port 8a is an oil supply port that supplies lubricating oil provided in the oil hole 7a. Similarly, the oil supply port 8b is an oil supply port that supplies lubricating oil provided in the oil hole 7b.
Then, at the start of starting the rotation of the reinforcing roll 1, high pressure (about 700 kgf / cm 2 ) lubricating oil is supplied to the oil pads 5, 5a and 5b provided on the inner surface of the bushing 4a.
[0014]
The operation of the oil film bearing of the present invention will be described with reference to FIG. FIG. 2 is a schematic cross-sectional view perpendicular to the roll axis at the central portion in the roll axis direction of the bushing 4a when the reinforcing roll is rotated.
The shaft center of the reinforcing roll is shifted to the left side of the vertical line passing through the center of the bushing 4a and stopped. At the start of rotation, the inner surface of the bushing 4a and the outer surface of the sleeve 2 are in contact with each other at the lower left corner. To do.
[0015]
In the oil film bearing of the present invention, at the time of starting to start the rotation of the reinforcing roll, high-pressure lubricating oil is supplied from the oil supply port to the lower oil pad 5 where the load acts through the oil holes 6 and 7, and another oil supply is performed. Supply the same high-pressure lubricating oil from the port to the right oil pad 5a through the oil holes 6a and 7a, and supply the same high-pressure lubricating oil from the other oil supply port to the left oil pad 5b through the oil holes 6b and 7b. To do.
[0016]
Since the axis of the reinforcing roll is displaced to the left of the vertical line passing through the center of the bushing 4, the distance between the left oil pad 5b and the outer surface of the sleeve 2 and the distance between the lower oil pad 5 and the outer surface of the sleeve 2 Is smaller than the distance between the right oil pad 5a and the outer surface of the sleeve 2. As a result, the levitation force for levitating the reinforcing roll acts diagonally upward to the right, so that the reinforcing roll floats diagonally upward to the right, and as shown in FIG. There is a gap between the outer surface. Therefore, when the reinforcing roll is rotated, seizure between the inner surface of the bushing 4a and the outer surface of the sleeve 2 at the lower left corner can be prevented.
[0017]
Thereafter, when the predetermined number of rotations of the reinforcing roll is reached, the supply of the lubricating oil to the oil pad 5 and the oil pads 5a, 5b is stopped at a high pressure, and the lubricating oil is supplied from another nozzle at a low pressure.
On the other hand, in the conventional oil film bearing shown in FIGS. 4 and 5, the axis of the reinforcing roll 1 is shifted to the left side of the vertical line passing through the center of the bushing 4 and stopped. When the outer surface of the sleeve 2 is in contact with the lower left diagonal portion, the lubricating oil supplied to the lower oil pad 5 on which the load acts cannot lift the reinforcing roll 1 diagonally upward to the right. As a result, when the reinforcing roll rotates, the inner surface of the bushing 4 and the outer surface of the sleeve 2 are seized at the lower left corner.
[0018]
In the above description, the axis of the reinforcing roll has been described in the case where it stops by shifting to the left side of the vertical line passing through the center of the bushing 4a, but the axis of the reinforcing roll is shifted to the right side of the vertical line passing through the center of the bushing 4a. Even when the oil film bearing is stopped, seizure between the outer surface of the sleeve 2 and the inner surface of the bushing 4a can be prevented by the same principle in the oil film bearing of the present invention. Moreover, although the case where the oil film bearing of the present invention was used for the lower reinforcing roll has been described, the upper reinforcing roll of the present invention is provided with at least one oil pad at the center in the roll axial direction of the upper inner surface of the bushing, In addition, seizure between the outer surface of the sleeve and the inner surface of the bushing can be achieved in the same manner by using an oil film bearing provided with at least one oil pad on both sides in the circumferential direction sandwiching the oil pad on the inner surface of the bushing. Can be prevented.
[0019]
In addition, by using the oil film bearing of the present invention for the work roll, seizure between the outer surface of the sleeve and the inner surface of the bushing can be similarly prevented.
[0020]
【The invention's effect】
According to the present invention, even when the roll axis does not coincide with the vertical line passing through the center of the bushing when the roll is stopped, seizure between the outer surface of the sleeve and the inner surface of the bushing can be prevented when the roll is rotated.
[Brief description of the drawings]
FIG. 1 is a schematic perspective view of a bearing box in which a bushing according to the present invention is housed.
FIG. 2 is a schematic sectional view for explaining the principle of the oil film bearing of the present invention.
FIG. 3 is a schematic front view showing the configuration of a four-high rolling mill using oil film bearings.
FIG. 4 is a schematic sectional view of a conventional oil film bearing in the roll axis direction.
FIG. 5 is a schematic cross-sectional view taken along the line XX of FIG.
[Explanation of symbols]
1 Reinforcing roll
10 Roll neck part 2 Sleeve 3, 3a Bearing box 4, 4a Bushing 5, 5a, 5b Oil pad 6, 6a, 6b Oil hole 7, 7a, 7b Oil hole 8, 8a, 8b Oil supply port

Claims (1)

軸受箱と、該軸受箱に内装された円筒状のブッシングと、ロールのロールネック部に外装されたスリーブとを備え、前記ブッシングの内部に前記スリーブを装着して、前記ブッシングの内面と前記スリーブの外面との隙間に潤滑油の油膜を形成する油膜軸受であって、前記ロールが回動自在にハウジングに支持された状態で、前記ロールの回転を開始する始動時には、オイルパッド（凹み）に前記ロールを浮上させ得る圧力で潤滑油を供給し、前記ロールの回転数が所定となったときには、オイルパッドに潤滑油を供給するのを停止し、別のノズルから前記ロールを浮上させ得る圧力よりも低圧で潤滑油を供給して前記隙間に潤滑油の油膜を形成するように構成され、
前記ブッシングの荷重が作用する方向の上部内面または下部内面のロール軸方向中央部に、少なくとも一つのオイルパッドを設け、該オイルパッドには前記ロールを浮上させ得る高圧の潤滑油を供給するハイドロスタティック潤滑装置が接続され、
それに加えてさらに、前記ブッシングの内面の荷重が作用する方向のオイルパッドを挟む円周方向の両側に、対称に前記ブッシングの中心と荷重が作用する方向のオイルパッドの円周方向中央とを結ぶ仮想線に対する中心角が45〜90°となる位置に円周方向中央が位置するようにそれぞれ少なくとも一つのオイルパッドを設け、前記ロールの回転を開始する始動時に、前記ブッシングの内面に設けられた荷重が作用する方向のオイルパッド及び該オイルパッドを挟んで円周方向両側に対称に設けたオイルパッドに前記ロールを浮上させ得る高圧の潤滑油を供給し、前記ロールを浮上させるようにしたことを特徴とする油膜軸受。A bearing box, a cylindrical bushing built in the bearing box, and a sleeve externally mounted on a roll neck of the roll, the sleeve being mounted inside the bushing, and the inner surface of the bushing and the sleeve An oil film bearing for forming an oil film of lubricating oil in a gap with the outer surface of the oil pad, and when the roll is supported by a housing so as to be rotatable, the oil pad (dent) is provided at the start of rotation of the roll. Lubricating oil is supplied at a pressure that allows the roll to float, and when the rotation speed of the roll reaches a predetermined value, the supply of the lubricating oil to the oil pad is stopped and the pressure that allows the roll to float from another nozzle The lubricating oil is supplied at a lower pressure than that to form a lubricating oil film in the gap,
At least one oil pad is provided at the center in the roll axial direction of the upper inner surface or the lower inner surface in the direction in which the load of the bushing acts, and the hydrostatic that supplies high-pressure lubricating oil capable of floating the roll to the oil pad is provided. The lubrication device is connected,
In addition, the center of the bushing and the center of the oil pad in the direction in which the load acts are symmetrically connected to both sides in the circumferential direction across the oil pad in the direction in which the load on the inner surface of the bushing acts. At least one oil pad is provided so that the center in the circumferential direction is located at a position where the central angle with respect to the imaginary line is 45 to 90 °, and provided at the inner surface of the bushing at the start of rotation of the roll . Supplying high-pressure lubricating oil capable of floating the roll to the oil pad in the direction in which the load acts and the oil pad provided symmetrically on both sides in the circumferential direction across the oil pad so that the roll is floated Oil film bearing characterized by
JP07131099A 1999-03-17 1999-03-17 Oil film bearing Expired - Fee Related JP4341103B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP07131099A JP4341103B2 (en) 1999-03-17 1999-03-17 Oil film bearing

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP07131099A JP4341103B2 (en) 1999-03-17 1999-03-17 Oil film bearing

Publications (2)

Publication Number Publication Date
JP2000263108A JP2000263108A (en) 2000-09-26
JP4341103B2 true JP4341103B2 (en) 2009-10-07

Family

ID=13456930

Family Applications (1)

Application Number Title Priority Date Filing Date
JP07131099A Expired - Fee Related JP4341103B2 (en) 1999-03-17 1999-03-17 Oil film bearing

Country Status (1)

Country Link
JP (1) JP4341103B2 (en)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6604859B1 (en) * 2002-01-23 2003-08-12 Morgan Construction Company Bushing for oil film bearing
DE102006016714A1 (en) 2006-04-08 2007-10-11 Sms Demag Ag Chock for receiving a roll neck
CN100464884C (en) * 2006-12-07 2009-03-04 郑红专 Self-lubricating segmental roller base
US9016099B2 (en) * 2011-09-29 2015-04-28 Siemens Industry, Inc. Hybrid hydrodynamic and hydrostatic bearing bushing and lubrication system for rolling mill
DE102011087605A1 (en) * 2011-12-01 2013-06-06 Sms Siemag Ag Chock and process for its manufacture
KR101324030B1 (en) 2012-07-23 2013-11-01 주식회사 제우스 Bearing housing having exhaust line of foreign substance
CN102840244B (en) * 2012-08-31 2015-04-08 太原重工股份有限公司 Bushing locating device for oil film bearing
CN105134781A (en) * 2014-08-08 2015-12-09 摩尔动力(北京)技术股份有限公司 Fluid directional suspension system
KR101777560B1 (en) * 2015-08-19 2017-09-13 (주) 파루 Rotation support device
AU2016201226B2 (en) * 2015-08-19 2017-10-12 Paru Co., Ltd. Rotation support apparatus
DE102015219752A1 (en) * 2015-10-13 2017-04-13 Sms Group Gmbh bearing bush

Also Published As

Publication number Publication date
JP2000263108A (en) 2000-09-26

Similar Documents

Publication Publication Date Title
JP4341103B2 (en) Oil film bearing
EP0007409A1 (en) Fluid bearing
JP2000170775A (en) Conical roller bearing and gear shaft support device for vehicle
GB2372078B (en) Half bearing with grooves preventing leakage of lubricating oil
EP0803657B1 (en) Reversing bearing device for double reversing propeller
JPH06280858A (en) Dynamic pressure bearing
CA1099324A (en) Bearing assembly and method
WO2001020183A1 (en) Self-aligned roller bearing
CN1863642B (en) Tapered roller bearing and method of machining tapered roller
JP2000130446A (en) Rolling bearing
JP2561402Y2 (en) Roller bearing
JP3609455B2 (en) Static pressure gas bearing
CA2465170C (en) Triple bearing arrangement for cantilevered roll shafts
JP3696673B2 (en) Universal joint
US2474489A (en) Rocker mounting for rotary bearings
JPH05105192A (en) Plain bearing for inner shaft of counter rotating propeller device
JPS58131427A (en) Journal bearing
JP2550266Y2 (en) Roller bearing removal device for roll support device of rolling mill
ITTO940001A1 (en) CROSS JOINT OF A HEART SHAFT SUITABLE FOR THE TRANSMISSION OF HIGH TORQUE MOMENTS.
JP3254904B2 (en) Horizontal rolling mill
KR200208012Y1 (en) Device for preventing eccentric of abrasive roll
JP2551646Y2 (en) Rolling mill
EP2100046B1 (en) A non-rotating shaft for a continuous casting machine
JPH0781586B2 (en) Oil film bearing with hydrostatic effect
JP3067407B2 (en) Rolling mill

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20051026

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20071214

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20071218

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20080218

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20090224

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20090427

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20090616

A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20090629

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20120717

Year of fee payment: 3

R150 Certificate of patent or registration of utility model

Free format text: JAPANESE INTERMEDIATE CODE: R150

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20120717

Year of fee payment: 3

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20130717

Year of fee payment: 4

LAPS Cancellation because of no payment of annual fees