JPH028081B2 - - Google Patents
Info
- Publication number
- JPH028081B2 JPH028081B2 JP4516582A JP4516582A JPH028081B2 JP H028081 B2 JPH028081 B2 JP H028081B2 JP 4516582 A JP4516582 A JP 4516582A JP 4516582 A JP4516582 A JP 4516582A JP H028081 B2 JPH028081 B2 JP H028081B2
- Authority
- JP
- Japan
- Prior art keywords
- curvature
- radius
- crane rail
- head
- profile
- 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
Links
- 210000001015 abdomen Anatomy 0.000 claims description 7
- 229910000831 Steel Inorganic materials 0.000 description 4
- 239000010959 steel Substances 0.000 description 4
- 238000012360 testing method Methods 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 239000002184 metal Substances 0.000 description 3
- 238000005452 bending Methods 0.000 description 2
- 230000007547 defect Effects 0.000 description 2
- 210000003371 toe Anatomy 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000012669 compression test Methods 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000009661 fatigue test Methods 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000001936 parietal effect Effects 0.000 description 1
- 238000005204 segregation Methods 0.000 description 1
- 238000009628 steelmaking Methods 0.000 description 1
Description
本発明は岸壁荷役クレーン、工場内外の天井走
行クレーンおよび地上走行クレーン、アンテナな
どの回転体の荷重支持などに使われているクレー
ンレールで、耐損傷性の優れたクレーンレールに
関するものである。
クレーンレールは電車、汽車などの軌道に使わ
れているレールに比べて極めて大きい輪重が加わ
つている。例えば製鋼の溶鋼を受ける受鋼台車や
溶鋼クレーンなどの輪重は70t程度のものも珍し
くはない。かかる大荷重が加えられると長期間使
用中に種々の損傷が発生する。それらを大別する
と第１図に示すように以下の４つになる。
第１図で、１はクレーンレール頭部内部割れ、
２は頭側部のメタルフロー、３は上首部き裂、４
は下首部き裂である。これらの損傷のうち２のメ
タルフローを除く３つはいずれも疲労き裂であ
る。これらは繰返し大荷重によつて生ずるのであ
るがその生成要因は細かく云えば少しずつ異な
る。
すなわち、１は大きな圧縮荷重によるせん断と
頭部水平方向の引張応力によつて、さらに頭部の
この部分は偏析等内部欠陥の集まりやすいことも
重畳して、かかる欠陥を起点にして内部割れが生
ずる。２は頭側部のメタルフローである。これは
大きな圧縮荷重が時には偏芯して加わるため頭側
部の塑性変形を伴う。かかる変形が生ずると車輪
のフランジを押し広げることになり、そのため安
定走行を妨げることがしばしば生ずる。
３および４は上首部と下首部の疲労き裂で偏芯
荷重による曲げ応力の繰返しに起因する。これら
の部分はウエブ（首部）と頭部または底部とを結
ぶ曲率止端部で、応力集中が起りやすい。
本発明はかかる問題点を解決するため従来のク
レーンレール形状を改善することによつて、耐損
傷性を向上せしめたものである。
第２図は従来クレーンレール形状である。第２
図ａはCR73Kg（長さ1m当りの重量）、ｂは
CR100Kgである。いずれも頭頂面、上首部そして
下首部の曲率半径R1＝1000，R2＝20，R3＝20mm
となつている。そこで、第１図に示すような損傷
の発生を防ぐために案出したのが本発明であつ
て、その代表例を第３図に示す。
第３図において、点線は第２図ａに示す従来の
クレーンレールである。第３図の実線から分るよ
うに、本発明の構成は、クレーンレールの断面形
状に於いて、頭頂面のプロフイールの曲率半径
R1が400〜800mmであり、腹部と頭部または底部
とを結ぶプロフイールの曲率半径R2，R3が30mm
以上であることを特徴としている。
クレーンレールの断面形状においてまず頭頂面
のプロフイールの曲率半径R1を400〜800mmと限
定した理由は、例えばクレーンに負荷が働いた場
合第４図で示すようにたわむ。一方、車輪とレー
ルとの接触応力を小さくするには接触面積を大き
くする必要がある。しかしながら、負荷が働いた
場合車輪軸もたわむので、もしクレーンレール頭
頂面を平坦にしていると、負荷時には明らかにク
レーンレールに偏芯荷重が働く。また頭頂面のプ
ロフイールの曲率半径を小さくとりすぎると逆に
面圧が上つてくる。本発明はこれを防ぐために設
けたもので車輪とレールとは球面接触するように
頭頂面のプロフイールの曲率半径R1の値を車輪、
車軸、軸受などの剛性から決定する必要がある。
この場合、車輪踏面もほぼ同一の曲率半径にする
ことが望ましい。次に、上首部つまり腹部から頭
部を結ぶプロフイールの曲率半径R2を30mm以上
と限定した理由は、偏芯荷重が働いた場合でも曲
率止端部の応力集中を緩和するためである。たと
え偏芯荷重が圧縮であつても塑性変形する位の大
きさであると、塑性変形によつて引張りの残留応
力が生ずるので、その後の繰返しで、疲労き裂が
発生伝播することは十分考えられる。それゆえ以
上の対策によつて第１図での損傷１，２，３およ
び４を防止することができる。
同様に下首部つまり腹部から底部にかけてのプ
ロフイールの曲率半径R3を30mm以上と限定の理
由もR2の場合と同じである。すなわち、偏芯荷
重による曲げモーメントが下首部に生じた場合で
も応力集中を緩和する目的である。
なお、本発明においては腹部と頭部を結ぶプロ
フイールの曲率半径R2が50mm以上で、腹部と底
部を結ぶプロフイールの曲率半径R3が30mm以上
であることが好ましい。
本発明によつて得られる効果を実施例でもつて
説明する。
実施例
第３図に示す本発明に従つた断面形状（R1＝
600mm、R2＝50mm、R3＝35mm）のクレーンレール
と第２図ａに示す従来の断面形状のクレーンレー
ルとを用いて試験した。素材はいずれもSS41で、
平削加工で製作した。試験片の長さは500mmで40
mm厚さの鉄板上に置き通常の治具で固定した。試
験機は150t万能疲労試験機を使用し、車輪の一部
から切出した治具で試験片の長さ方向の中央、巾
方向の1/4の部分を押しつけた。それがためにク
レーンレールを巾方向で3゜傾けた。繰返し圧縮速
度は500cpm（サイクル／分）である。損傷の発生
は200×104回繰返し後カラーチエツクで確めた。
実験結果を第１表に示す。
The present invention relates to a crane rail that has excellent damage resistance and is used for supporting loads of rotating bodies such as quay cargo handling cranes, overhead cranes and ground traveling cranes inside and outside of factories, and antennas. Crane rails have an extremely large wheel load compared to the rails used for trains, trains, etc. For example, it is not uncommon for the wheel weight of steel receiving carts and molten steel cranes, which receive molten steel in steelmaking, to be around 70 tons. When such a large load is applied, various damages occur during long-term use. They can be roughly divided into the following four types, as shown in Figure 1. In Figure 1, 1 indicates a crack inside the crane rail head.
2 is a metal flow on the side of the head, 3 is a crack in the upper neck, 4 is
is a lower neck crack. All three of these damages, except for metal flow (2), are fatigue cracks. These are caused by repeated heavy loads, but the factors that cause them differ slightly. In other words, 1 is caused by the shear caused by the large compressive load and the tensile stress in the horizontal direction of the head, and also because internal defects such as segregation tend to collect in this part of the head, causing internal cracks to start from such defects. arise. 2 is the metal flow on the side of the head. This is accompanied by plastic deformation of the side of the head because a large compressive load is sometimes applied eccentrically. When such deformation occurs, the flanges of the wheels are forced apart, which often impedes stable driving. Nos. 3 and 4 are fatigue cracks in the upper neck and lower neck, which are caused by repeated bending stress caused by eccentric loads. These parts are toes of curvature that connect the web (neck) and the head or bottom, and are prone to stress concentration. In order to solve this problem, the present invention improves the damage resistance by improving the shape of the conventional crane rail. Figure 2 shows the shape of a conventional crane rail. Second
Figure a is CR73Kg (weight per 1m length), b is
CR100Kg. In both cases, the radius of curvature of the parietal surface, upper neck, and lower neck is R 1 = 1000, R 2 = 20, R 3 = 20 mm.
It is becoming. Therefore, the present invention was devised to prevent the occurrence of damage as shown in FIG. 1, and a typical example thereof is shown in FIG. In FIG. 3, the dotted line is the conventional crane rail shown in FIG. 2a. As can be seen from the solid line in FIG.
R 1 is 400 to 800 mm, and the radius of curvature R 2 and R 3 of the profile connecting the abdomen and the head or bottom is 30 mm.
It is characterized by the above. The reason why the radius of curvature R 1 of the profile of the top of the crane rail is limited to 400 to 800 mm in the cross-sectional shape of the crane rail is that, for example, when a load is applied to the crane, it deflects as shown in FIG. 4. On the other hand, in order to reduce the contact stress between the wheels and the rails, it is necessary to increase the contact area. However, when a load is applied, the wheel axle also bends, so if the top surface of the crane rail is made flat, an eccentric load will obviously be applied to the crane rail when the crane rail is loaded. Furthermore, if the radius of curvature of the profile on the top of the head is made too small, the surface pressure will increase. The present invention was provided to prevent this, and the value of the radius of curvature R 1 of the profile of the top surface of the wheel is adjusted so that the wheel and the rail are in spherical contact.
It must be determined based on the rigidity of the axle, bearings, etc.
In this case, it is desirable that the wheel treads also have approximately the same radius of curvature. Next, the reason why the radius of curvature R 2 of the profile connecting the upper neck, that is, the abdomen to the head, is limited to 30 mm or more is to alleviate stress concentration at the toe of curvature even when an eccentric load is applied. Even if the eccentric load is compressive, if it is large enough to cause plastic deformation, the plastic deformation will generate tensile residual stress, so it is highly unlikely that fatigue cracks will develop and propagate with subsequent repetition. It will be done. Therefore, by taking the above measures, damages 1, 2, 3 and 4 in FIG. 1 can be prevented. Similarly, the reason why the radius of curvature R3 of the profile from the lower neck, that is, from the abdomen to the bottom, is limited to 30 mm or more is the same as for R2 . That is, the purpose is to alleviate stress concentration even when a bending moment due to an eccentric load occurs in the lower neck portion. In the present invention, it is preferable that the radius of curvature R 2 of the profile connecting the abdomen and the head is 50 mm or more, and the radius of curvature R 3 of the profile connecting the abdomen and the bottom is 30 mm or more. The effects obtained by the present invention will be explained using examples. Example A cross-sectional shape according to the invention shown in FIG. 3 (R 1 =
The test was conducted using a crane rail with a diameter of 600 mm, R 2 = 50 mm, R 3 = 35 mm) and a crane rail with a conventional cross-sectional shape shown in Figure 2a. All materials are SS41,
Manufactured by planing. The length of the test piece is 500 mm and 40
It was placed on a steel plate with a thickness of mm and fixed with a regular jig. A 150t universal fatigue testing machine was used as the testing machine, and a jig cut out from a part of a wheel was used to press against the center of the test piece in the length direction and 1/4 of the width. To do this, the crane rail was tilted 3 degrees in the width direction. The cyclic compression rate is 500 cpm (cycles/minute). The occurrence of damage was confirmed by color check after repeating 200×10 4 times.
The experimental results are shown in Table 1.
【表】
第１表の結果から明らかなように本発明の場
合、従来法に比較して優れている。[Table] As is clear from the results in Table 1, the present invention is superior to the conventional method.
第１図はクレーンレールにおける損傷発生の部
位を示す断面説明図、第２図は従来のクレーンレ
ーンレールの断面の寸法形状を示す図で、ａは
CR73Kg、ｂはCR100Kg、第３図は本発明クレー
ンレールの実施例の断面図、第４図は繰返し圧縮
試験の態様を示す図である。
Fig. 1 is a cross-sectional explanatory diagram showing the location of damage in the crane rail, Fig. 2 is a diagram showing the dimensions and shape of the cross section of a conventional crane lane rail, and a is
CR73Kg, b is CR100Kg, FIG. 3 is a cross-sectional view of an embodiment of the crane rail of the present invention, and FIG. 4 is a diagram showing an aspect of a repeated compression test.
Claims (1)
のプロフイールの曲率半径R1が400〜800mmであ
り、腹部と頭部を結ぶプロフイールの曲率半径
R2および腹部と底部を結ぶプロフイールの曲率
半径R3が夫々30mm以上であることを特徴とする
耐損傷性の優れたクレーンレール。1 In the cross-sectional shape of the crane rail, the radius of curvature R 1 of the profile on the top of the head is 400 to 800 mm, and the radius of curvature of the profile connecting the abdomen and head is
A crane rail with excellent damage resistance characterized by R 2 and radius of curvature R 3 of the profile connecting the abdomen and the bottom each being 30 mm or more.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4516582A JPS58164801A (en) | 1982-03-20 | 1982-03-20 | Crane rail excellent in damage resistance |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4516582A JPS58164801A (en) | 1982-03-20 | 1982-03-20 | Crane rail excellent in damage resistance |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS58164801A JPS58164801A (en) | 1983-09-29 |
| JPH028081B2 true JPH028081B2 (en) | 1990-02-22 |
Family
ID=12711645
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4516582A Granted JPS58164801A (en) | 1982-03-20 | 1982-03-20 | Crane rail excellent in damage resistance |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58164801A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6555689B2 (en) | 1993-06-25 | 2003-04-29 | Merrell Pharmaceuticals Inc. | Intermediates useful for the preparation of antihistaminic piperidine derivatives |
-
1982
- 1982-03-20 JP JP4516582A patent/JPS58164801A/en active Granted
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6555689B2 (en) | 1993-06-25 | 2003-04-29 | Merrell Pharmaceuticals Inc. | Intermediates useful for the preparation of antihistaminic piperidine derivatives |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS58164801A (en) | 1983-09-29 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4853999A (en) | Tail bridge | |
| JPS6243914B2 (en) | ||
| JPH028081B2 (en) | ||
| US3712250A (en) | Tank structure | |
| RU2566798C2 (en) | Freight car bogie side frame of built-up structure and method of its production | |
| US10913469B2 (en) | Railroad car truck bolster | |
| CN108516372B (en) | Inclined boarding bridge for loading and unloading | |
| CN217799733U (en) | Production line of railway wagon end wall | |
| CN115583577A (en) | Rail steering device, cart traveling mechanism and shore bridge | |
| US3744434A (en) | Schnabel-type railroad car | |
| EP3544909B1 (en) | Support and storage stand for heavy cylindrical loading material | |
| JP3495095B2 (en) | Mooring roller for floating structure with elastic cushioning material | |
| MX2008004818A (en) | Crane with reinforcing plate. | |
| CN109422067B (en) | Chain self-guiding centering device of chain conveyor and preparation method thereof | |
| CN218595889U (en) | Auxiliary device for hoisting box girder | |
| CN218930525U (en) | Girder transferring tool | |
| CN216509747U (en) | Auxiliary tool rack for transportation | |
| US20200391772A1 (en) | Railcar cover plate | |
| CN218145427U (en) | Truss structure lifted by adopting slide way | |
| CN211895730U (en) | Steering and track-entering mechanism for cart walking | |
| US2349373A (en) | Trailer axle | |
| CN111573513B (en) | Flexible sheet member turning-over method | |
| CN210943429U (en) | Conveyor is used in steel ingot production | |
| CN209956305U (en) | Movable board packaging vehicle | |
| JPS645691A (en) | Method for improving formability of joint stock in laser beam welding |