JPS61171917A - Multi-row roller bearing - Google Patents
Multi-row roller bearingInfo
- Publication number
- JPS61171917A JPS61171917A JP60012091A JP1209185A JPS61171917A JP S61171917 A JPS61171917 A JP S61171917A JP 60012091 A JP60012091 A JP 60012091A JP 1209185 A JP1209185 A JP 1209185A JP S61171917 A JPS61171917 A JP S61171917A
- Authority
- JP
- Japan
- Prior art keywords
- roller
- row
- rollers
- load
- bearing
- 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.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/34—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load
- F16C19/38—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers
- F16C19/383—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
- F16C19/385—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for both radial and axial load with two or more rows of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone with two rows, i.e. double-row tapered roller bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/50—Other types of ball or roller bearings
- F16C19/505—Other types of ball or roller bearings with the diameter of the rolling elements of one row differing from the diameter of those of another row
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/541—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing
- F16C19/542—Systems consisting of juxtaposed rolling bearings including at least one angular contact bearing with two rolling bearings with angular contact
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2322/00—Apparatus used in shaping articles
- F16C2322/12—Rolling apparatus, e.g. rolling stands, rolls
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
この発明は、多列ころ軸受に関し、とくに、各ころ列に
不均等な荷重が負荷される多列ころ軸受において、大荷
重が負荷される特定のころ列の負荷容量を増大して、各
ころ列の軸受寿命の均一化を図り、もって軸受寿命を延
長するようにしたものである。[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to multi-row roller bearings, and particularly to multi-row roller bearings in which uneven loads are applied to each roller row, and in which large loads are applied. The load capacity of a specific roller row is increased to equalize the bearing life of each roller row, thereby extending the bearing life.
一般に、多列ころ軸受は、たとえば圧延機の圧延ロール
、バックアップロールなどのロールネック用軸受として
広く使用されているが、従来、この種のロールネック用
軸受としては、主として第２図に示すような４列円すい
ころ軸受を組付けている。同図において、符号１は圧延
機のロール、２はロールネックをそれぞれ示し、ロール
ネック２を半径方向に支持する４列円すいころ軸受４は
、軸受箱（チョック）３によって保持されている。In general, multi-row roller bearings are widely used as bearings for roll necks such as rolling rolls and backup rolls of rolling mills. A four-row tapered roller bearing is installed. In the figure, reference numeral 1 indicates a roll of a rolling mill, and reference numeral 2 indicates a roll neck. Four-row tapered roller bearings 4 that support the roll neck 2 in the radial direction are held by a bearing box (chock) 3.
この円すいころ軸受４は、２個の複列内輪５と２個の単
列外輪６．１個の複列外輪７との間に、４列の円す？）
ころ８を組付けたものであるが、円すいころ８は、各こ
ろ列とも材料、形状および寸法が同一仕様のものを、同
一ころ数ずつ配設している。また軸受箱３は、受は部材
９ａに対して曲面で接触する支持部材９ｂを介して支持
されており、軸受箱３がロール１のたわみに追従して傾
くことができるような調心機構を設けている。さらに、
最近の圧延機においては、ロール１を軸方向に移動させ
る機構を設けたものが開発されており、このような機構
を設けた圧延機のロールネック用軸受は、ロール１が軸
方向に移動すると、軸受中心に対して偏位したモーメン
ト荷重が負荷される。This tapered roller bearing 4 has four rows of circular rings between two double-row inner rings 5, two single-row outer rings 6, and one double-row outer ring 7. )
The rollers 8 are assembled, and the tapered rollers 8 have the same specifications in material, shape, and dimensions in each roller row, and the same number of tapered rollers are arranged. The bearing box 3 is supported via a support member 9b that contacts the member 9a on a curved surface, and has an alignment mechanism that allows the bearing box 3 to tilt following the deflection of the roll 1. It is set up. moreover,
Recent rolling mills have been developed that are equipped with a mechanism that moves the roll 1 in the axial direction. , a moment load deviated from the center of the bearing is applied.
上記のように、軸受箱３の調心機構を設けたロールネッ
ク用軸受においては、調心機構が正常に作動すれば、ロ
ール１の軸心と軸受箱３の中心軸との相対的傾きが生ず
ることはないから、軸受の各ころ列には均等な荷重が負
荷されることになるが、実際には、調心機構の受部材９
ａと支持部材９ｂとの間の摩擦力の影響などによって、
ロール１の傾きに対する軸受箱３の追従が十分には行な
われないことが多く、軸受箱３の中心軸がロール１の軸
心に一致しない状態で負荷を受けるという事態が発生す
る。As mentioned above, in a roll neck bearing equipped with an alignment mechanism for the bearing box 3, if the alignment mechanism operates normally, the relative inclination between the axis of the roll 1 and the central axis of the bearing box 3 will be Since this does not occur, an equal load is applied to each roller row of the bearing, but in reality, the bearing member 9 of the alignment mechanism
Due to the influence of the frictional force between a and the support member 9b,
In many cases, the bearing box 3 does not follow the inclination of the roll 1 sufficiently, and a situation occurs in which the center axis of the bearing box 3 is not aligned with the axis of the roll 1 and receives a load.
このため、各ころ列の荷重は、たとえば第３図に示すよ
うに、特定のころ列（バレル側から２列目のＢ列と４列
目のＤ列）に大きな荷重が負荷されるのに対し、その他
のＡ列と０列とに負荷される荷重は小さくな一す、軸受
全体としては、きわめて不均等な荷重分布になる。その
結果、大きな荷重が負荷されるころ列では、定格負荷以
上の荷重が負荷され、またエツジロードが生じて早期は
くりやスミアリング等による損傷が起り、各ころ列毎の
寿命時間が不均一になるという問題がある。Therefore, as shown in Figure 3, the load on each roller row is large, even though a large load is applied to a specific roller row (row B, the second row from the barrel side, and row D, the fourth row from the barrel side). On the other hand, the load applied to the other rows A and 0 is small, and the load is distributed very unevenly throughout the bearing. As a result, on roller rows that are subjected to large loads, loads exceeding the rated load are applied, and edge loading occurs, causing damage such as premature peeling and smearing, and the lifespan of each row of rollers becomes uneven. There is a problem.
また、ロール１を軸方向に移動させる機構を設けた場合
においては、第４図および第５図に示すような荷重分布
の不均等が生ずることになる。すなわち、第４図（ａ）
のようにロール１の軸方向移動によって、軸受の軸方向
の中心位置０−０に対して負荷中心Ｐがバレル側に偏位
した場合は、同図中）に示すようにＢ列の荷重が最大と
なるが、これと反対に、第５図（ａ）のように軸受の軸
方向の中心位置０−０に対して負荷中心Ｐが軸端側に偏
位した場合は、同図中）に示すように０列の荷重が最大
となる。Furthermore, if a mechanism for moving the roll 1 in the axial direction is provided, an uneven load distribution will occur as shown in FIGS. 4 and 5. That is, FIG. 4(a)
When the load center P deviates toward the barrel side with respect to the axial center position 0-0 of the bearing due to the axial movement of the roll 1, as shown in the figure), the load in the B row is However, on the contrary, if the load center P deviates to the shaft end side with respect to the axial center position 0-0 of the bearing as shown in Fig. 5 (a), As shown in , the load on the 0th row is the maximum.
したがって、特にロールの移動機構が設けられた圧延機
の・−ルネ・り用軸受においては、・−【ルのたわみと
モーメント荷重とによって、各ころ列の荷重分布の不均
等がますます著しくなり、軸受の早期破損を助長する結
果となっている。Therefore, especially in rolling mill bearings equipped with a roll movement mechanism, the unevenness of the load distribution on each roller row becomes increasingly significant due to the deflection and moment load of the rollers. , which promotes early bearing failure.
この発明は、上記のような問題を解決するためになされ
たものであり、この発明の目的は、大荷重が負荷される
ころ列の負荷容量を増大して、使用時における各ころ列
の軸受寿命を均等に近づけるようにし、もって軸受全体
の寿命の延長を図った多列ころ軸受を提供することにあ
る。This invention was made to solve the above-mentioned problems, and an object of the invention is to increase the load capacity of the roller rows to which large loads are applied, and to improve the bearing capacity of each roller row during use. To provide a multi-row roller bearing whose lifespans are made nearly uniform, thereby extending the lifespan of the entire bearing.
内輪と外輪との間の軸方向に複数列のころが配設され、
各ころ列に異なる大きさの荷重が負荷される箇所に使用
される多列ころ軸受において、大荷重が負荷される特定
のころ列のころの長さ、直径およびころ数のうち少なく
とも一つを、小荷重が負荷されるころ列のころの長さ、
直径よりも大きく、ころ数よりも多数とする。Multiple rows of rollers are arranged in the axial direction between the inner ring and outer ring,
In multi-row roller bearings used where loads of different magnitudes are applied to each roller row, at least one of the length, diameter, and number of rollers of a specific roller row to which a large load is applied is determined. , the length of the rollers in the row of rollers to which a small load is applied,
It should be larger than the diameter and more than the number of rollers.
第１図は、この発明を、前記第４図および第５図で説、
明したロールを軸方向に移動させる移動機構の設けられ
た圧延装置に用いる一形式の４列円すいころ軸受に適用
した実施例を示す縦断面図である。FIG. 1 illustrates the present invention with reference to FIGS. 4 and 5.
FIG. 2 is a longitudinal cross-sectional view showing an embodiment applied to a type of four-row tapered roller bearing used in a rolling machine equipped with a moving mechanism for moving the rolls described above in the axial direction.
この円すいころ軸受は、２個の複列円すいころ軸受１０
ａ、１０ｂを、中間に１個の内輪間座２０と２個の外輪
間座２２．２３とを介在させて装置（図示せず）に組付
けた構成になっている。内輪間座２０および外輪間座２
２．２３には、それぞれ油穴２１．２４が設けてあり、
外輪間座２２゜２３にはそれぞれオイルシール２５，２
６を嵌込んでそのリップを内輪間座２０に摺接させであ
る。This tapered roller bearing consists of two double row tapered roller bearings 10
a, 10b are assembled into a device (not shown) with one inner ring spacer 20 and two outer ring spacers 22, 23 interposed between them. Inner ring spacer 20 and outer ring spacer 2
2.23 has oil holes 21.24 respectively,
Oil seals 25 and 2 are installed on the outer ring spacers 22 and 23, respectively.
6 is fitted and its lip is brought into sliding contact with the inner ring spacer 20.
また前記内輪１１ａ、ｌｌｂには、らせん状の油溝３１
が刻設されている。In addition, a spiral oil groove 31 is provided in the inner rings 11a and llb.
is engraved.
上記の複列円すいころ軸受１０ａ、１０ｂの内輪１１ａ
、ｌｌｂは、２列の軌道を一体にした複列内輪であるが
、外輪１２ａ、１３ａ；１２ｂ。Inner ring 11a of the above double row tapered roller bearings 10a, 10b
, llb are double-row inner rings that integrate two rows of raceways, and outer rings 12a, 13a; 12b.
１３ｂは各列の軌道が別個になった単列外輪であって、
２個の外輪の間に袖穴１４ａ、１４ｂ付きの間座１５ａ
、１５ｂが挿入されている。13b is a single row outer ring in which each row has a separate raceway,
Spacer 15a with sleeve holes 14a and 14b between two outer rings
, 15b are inserted.
一方の複列円すいころ軸受１０ａの内輪１１ａと外輪１
２ａ、’１３ａとの軌道面と、他方の複列円すいころ軸
受１０ｂの内輪１１ｂと外輪１２ｂ。Inner ring 11a and outer ring 1 of one double-row tapered roller bearing 10a
2a and '13a, and the inner ring 11b and outer ring 12b of the other double-row tapered roller bearing 10b.
１３ｂとの軌道面との断面形状は、各軌道列（ころ列）
とも軸受中心側の大端径寸法が同一であって、軌道母線
の勾配も同一であるが、各ころ列の軌道母線の長さが異
なっており、一方の複列円すいころ軸受１０ａでは右列
の軌道母線が左列の軌道母線よりも長く、他方の複列円
すいころ軸受１０ｂでは、これと反対に左列の軌道母線
が右列の軌道母線よりも長（、それぞれの軸受の右列と
左列との軌道面は、左右対称の断面形状になっている。The cross-sectional shape of 13b and the raceway surface is for each raceway row (roller row).
Both have the same large end diameter on the center side of the bearings and the same slope of the raceway generatrix, but the lengths of the raceway generatrix of each roller row are different, and in the case of the double-row tapered roller bearing 10a, In the other double-row tapered roller bearing 10b, the raceway generatrix of the left row is longer than the raceway generatrix of the right row. The raceway surface with the left row has a symmetrical cross-sectional shape.
上記の一方の複列円すいころ軸受１０ａの内輪１１ａと
外輪１２ａ、１３ａとの間の軌道面には、各列の軌道面
の断面形状に対応する直径および長さ寸法に成形された
円すいころ１６ａ、１７ａが組み込まれ、他方の複列円
すいころ軸受１０ｂの内輪１１ｂと外輪１２ｂ、１３ｂ
との間の軌道面にも同様に、各列の軌道面の断面形状に
対応する直径および長さ寸法に成形された円すいころ１
６ｂ、１７ｂが組み込まれている。On the raceway surface between the inner ring 11a and the outer rings 12a, 13a of the double-row tapered roller bearing 10a, tapered rollers 16a are formed to have a diameter and length corresponding to the cross-sectional shape of the raceway surface of each row. , 17a are incorporated, and the inner ring 11b and outer rings 12b, 13b of the other double-row tapered roller bearing 10b
Similarly, tapered rollers 1 are formed on the raceway surfaces between the
6b and 17b are incorporated.
上記の２個の複列円すいころ軸受１０ａ、１０ｂを組合
わせて、ころ列を４列に構成した円すいころ軸受は、左
端側から数えて１番目のころ列と４番目のころ列との円
すいころ１６ａ、１６ｂが同一寸法形状のものであり、
２番目のころ列と３番目のころ列との円すいころ１７ａ
、１７ｂが同一寸法形状のものであるが、第２列および
第３列の軌道面には、第１列および第４列の円すいころ
よりもころ長さの長いころがそれぞれ配設されることに
なる。A tapered roller bearing in which the two double-row tapered roller bearings 10a and 10b described above are combined to form four rows of rollers is a tapered roller bearing that has four rows of rollers counted from the left end. The rollers 16a and 16b have the same size and shape,
Tapered rollers 17a in the second roller row and third roller row
, 17b are of the same size and shape, but rollers having longer roller lengths than the tapered rollers of the first and fourth rows are arranged on the raceway surfaces of the second and third rows, respectively. become.
なお、上図において、符号１８ａ、１９ａ；１８ｂ、１
９ｂは、それぞれ保持器を示す。In addition, in the above figure, symbols 18a, 19a; 18b, 1
9b each indicates a retainer.
上記のようにして構成された４列円すいころ軸受を、た
とえば圧延機のロールネックに組付けて使用する場合、
ロールのたわみやモーメント荷重によって各ころ列に負
荷される荷重分布が不均等になるが、いま第２列と第３
列とのころ列に、第１列と第４列とのころ列よりも大き
な荷重が負荷 吏されるものとする。When using the four-row tapered roller bearing configured as described above, for example, by assembling it into the roll neck of a rolling mill,
The load distribution applied to each row of rollers becomes uneven due to deflection of the rolls and moment load.
It is assumed that a larger load is applied to the roller rows of the first row and the fourth row than the roller rows of the first and fourth rows.
４列円すいころ軸受のころ列に上記のような不均等な荷
重分布が生じた場合においても、第２列と第３列とのこ
ろ列の円すいころ１７ａ、１７ｂは、第１列と第４列と
のころ列の円すいころ１６ａ、１６ｂよりもころ長さを
長くして軌道面との接触長さを大きくしているので、第
２列と第３列とのころ列の負荷容量は、第１列と第４列
とのころ列の負荷容量よりも大きくなっている。したが
って、第２列と第３列との軌道面の接触圧力が緩和され
、第１列と第４列との軌道面の接触圧力に近づく方向へ
機能する。Even when the above-mentioned uneven load distribution occurs in the roller rows of a four-row tapered roller bearing, the tapered rollers 17a and 17b of the second and third rows are Since the length of the rollers is longer than that of the tapered rollers 16a and 16b of the roller rows and the contact length with the raceway surface is increased, the load capacity of the roller rows of the second and third rows is as follows. It is larger than the load capacity of the first and fourth roller rows. Therefore, the contact pressure between the raceway surfaces of the second row and the third row is relaxed, and the contact pressure between the raceway surfaces of the first row and the fourth row functions in a direction closer to that of the raceway surfaces.
上記実施例では、大荷重が負荷されるころ列のころの長
さを長くすることによって、軌道面との接触長さを大き
くして負荷容量を増大させる場合について説明したが、
この発明は、上記実施例のほか、大荷重が負荷されるこ
ろ列に配設するころの数を、小荷重が負荷されるころ列
のころ数よりも多数にしても、全く同様の理由によって
同等の作用効果を得ることができる。In the above embodiment, a case was explained in which the load capacity is increased by increasing the length of the rollers in the roller row to which a large load is applied, thereby increasing the contact length with the raceway surface.
In addition to the above-mentioned embodiments, this invention also allows for the same reason even if the number of rollers disposed in a row of rollers to which a large load is applied is greater than the number of rollers in a row of rollers to which a small load is applied. Equivalent effects can be obtained.
また、この発明は、大荷重が負荷されるころ列に、小荷
重が負荷されるころ列のころよりも直径の大きいころを
配設するか、あるいは、ころ長さと直径との双方を大き
くしたころを配設してもよく、このようにした場合にお
いても、同様に当該ころ列の負荷容量を増大させること
ができる。In addition, the present invention provides rollers having a larger diameter than rollers in a roller row to which a small load is applied, or rollers in which both the length and diameter of the rollers are increased. Rollers may be provided, and even in this case, the load capacity of the roller row can be similarly increased.
なお、この発明は、円すいころ軸受に限らず、その他の
円筒ころ軸受、針状ころ軸受およびこれらを組合わせた
多列ころ軸受などについても適用することができる。ま
た第２図に示した従来形式の４列円すいころ軸受にもそ
のまま適用できるものである。Note that the present invention is applicable not only to tapered roller bearings but also to other cylindrical roller bearings, needle roller bearings, and multi-row roller bearings that are a combination of these. It can also be applied as is to the conventional four-row tapered roller bearing shown in FIG.
以上、説明したように、この発明によれば、多列ころ軸
受のころ列の負荷容量を、ころ列毎に異なる荷重条件に
応じて設定することができるから、特定のころ列に他の
ころ列よりも大きな荷重が負荷される場合においても、
前記の重荷重やエツジロードなどによる早期ばくりゃス
ミアリング等による損傷が生ずることが少なく、各ころ
列の寿命時間が平均化に近づき、全体としての軸受寿命
が長くなり、信頼性の高い多列ころ軸受を得ることがで
きる。したがって、この発明の多列ころ軸受は、圧延機
のロールネック用として最も好適な性能を有する軸受と
なる。As explained above, according to the present invention, the load capacity of the roller rows of a multi-row roller bearing can be set according to different load conditions for each roller row. Even when a load larger than the column is applied,
Early exposure due to heavy loads and edge loads is less likely to cause damage due to smearing, etc., and the lifespan of each row of rollers approaches an average, resulting in a longer bearing life as a whole, resulting in highly reliable multi-row rollers. You can get bearings. Therefore, the multi-row roller bearing of the present invention has the most suitable performance for the roll neck of a rolling mill.
第１図は、この発明の実施例を示す上半縦断面図、第２
図は、圧延機のロールネック用軸受の従来例を示す縦断
面図、第３図は、ロールネック用軸受の各ころ列の荷重
分布図、第４図および第５図は、それぞれロール移動型
圧延機のロール移動時における負荷状態を示し、第４図
（ａ）および第５図（ａ）は、それぞれ負荷中心位置図
、第４図（ｂ）および第５図（ｂ）は、それぞれ各ころ
列の荷重分布図である。
図中、１１ａ、１１ｂは内輪、１２ａ、１３ａｉ１２ｂ
、１３ｂは外輪、１６ａ、１６ｂは、それぞれころ長さ
の短い円すいころ、１７ａ、１７ｂはそれぞれころ長さ
の長い円すいころである。
特許出願人 日本精工株式会社
代理人 弁理士 森 哲 也
代理人 弁理士 内 藤 嘉 昭
代理人 弁理士 清 水 正
暴奪Ｗ擲
ｔ
（ｂ）
（ｂ）
ＢＣＤFIG. 1 is an upper half vertical sectional view showing an embodiment of the present invention, and FIG.
The figure is a vertical cross-sectional view showing a conventional example of a roll neck bearing for a rolling mill, Figure 3 is a load distribution diagram of each row of rollers of a roll neck bearing, and Figures 4 and 5 are of the roll moving type. The load state during roll movement of the rolling mill is shown, and FIGS. 4(a) and 5(a) are load center position diagrams, respectively, and FIGS. 4(b) and 5(b) are respectively load center position diagrams. It is a load distribution diagram of a roller row. In the figure, 11a and 11b are inner rings, 12a and 13ai12b
, 13b are outer rings, 16a and 16b are tapered rollers with short roller lengths, and 17a and 17b are tapered rollers with long roller lengths. Patent Applicant NSK Ltd. Representative Patent Attorney Tetsuya Mori Patent Attorney Yoshiaki Naito Representative Patent Attorney Masashi Shimizu (b) (b) BCD
Claims (1)
各ころ列に異なる大きさの荷重が負荷される多列ころ軸
受において、大荷重が負荷されるころ列のころの長さ、
直径およびころ数のうち少なくとも一つを、小荷重が負
荷される特定のころ列のころの長さ、直径よりも大きく
、ころ数よりも多数としたことを特徴とする多列ころ軸
受。Multiple rows of rollers are arranged on the raceway between the inner and outer rings,
In multi-row roller bearings in which different loads are applied to each roller row, the length of the rollers in the roller row to which a large load is applied,
A multi-row roller bearing characterized in that at least one of the diameter and the number of rollers is larger than the length and diameter of the rollers of a specific roller row to which a small load is applied, and larger than the number of rollers.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60012091A JP2564261B2 (en) | 1985-01-25 | 1985-01-25 | Rolling mill roll neck bearing support device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60012091A JP2564261B2 (en) | 1985-01-25 | 1985-01-25 | Rolling mill roll neck bearing support device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61171917A true JPS61171917A (en) | 1986-08-02 |
| JP2564261B2 JP2564261B2 (en) | 1996-12-18 |
Family
ID=11795897
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60012091A Expired - Lifetime JP2564261B2 (en) | 1985-01-25 | 1985-01-25 | Rolling mill roll neck bearing support device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2564261B2 (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005147408A (en) * | 2005-01-11 | 2005-06-09 | Ntn Corp | Double row rolling bearing |
| JP2005337267A (en) * | 2004-02-20 | 2005-12-08 | Mitsubishi Heavy Ind Ltd | Revolving wheel bearing structure for windmill |
| WO2006033320A1 (en) * | 2004-09-21 | 2006-03-30 | Ntn Corporation | Double-row self-aligning roller bearing and main shaft support structure for wind-turbine generator |
| WO2006080127A1 (en) * | 2005-01-25 | 2006-08-03 | Ntn Corporation | Helical gear support structure, speed increaser for wind power generation plant, and vertical shaft support structure |
| EP1705392A1 (en) * | 2003-11-18 | 2006-09-27 | Ntn Corporation | Double-row self-aligning roller bearing and device for supporting wind turbine generator main shaft |
| WO2007095953A1 (en) * | 2006-02-24 | 2007-08-30 | Vestas Wind Systems A/S | Gearbox for a wind turbine, bearing and method of manufacturing a bearing |
| US7927019B2 (en) | 2005-05-31 | 2011-04-19 | Mitsubishi Heavy Industries Ltd. | Slewing bearing structure |
| CN102619875A (en) * | 2012-04-10 | 2012-08-01 | 济南轨道交通装备有限责任公司 | Self-aligning roller bearing for main shaft of wind turbine generator and design method thereof |
| CN102829076A (en) * | 2011-06-14 | 2012-12-19 | 瓦房店正达冶金轧机轴承有限公司 | Sealed four-row cylinder bearing |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5397701U (en) * | 1977-01-12 | 1978-08-08 | ||
| JPS5471250A (en) * | 1977-09-28 | 1979-06-07 | Skf Ind Trading & Dev | Roller bearing |
| JPS5594022A (en) * | 1978-12-21 | 1980-07-17 | Timken Co | Multiirow bearing |
| JPS5790416A (en) * | 1980-11-26 | 1982-06-05 | Nachi Fujikoshi Corp | Monobloc type plural rows cone roller bearing and its assembly procedure |
-
1985
- 1985-01-25 JP JP60012091A patent/JP2564261B2/en not_active Expired - Lifetime
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5397701U (en) * | 1977-01-12 | 1978-08-08 | ||
| JPS5471250A (en) * | 1977-09-28 | 1979-06-07 | Skf Ind Trading & Dev | Roller bearing |
| JPS5594022A (en) * | 1978-12-21 | 1980-07-17 | Timken Co | Multiirow bearing |
| JPS5790416A (en) * | 1980-11-26 | 1982-06-05 | Nachi Fujikoshi Corp | Monobloc type plural rows cone roller bearing and its assembly procedure |
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7918649B2 (en) | 2003-11-18 | 2011-04-05 | Ntn Corporation | Double-row self-aligning roller bearing and device for supporting wind turbine generator main shaft |
| EP1705392A1 (en) * | 2003-11-18 | 2006-09-27 | Ntn Corporation | Double-row self-aligning roller bearing and device for supporting wind turbine generator main shaft |
| EP1705392A4 (en) * | 2003-11-18 | 2007-05-30 | Ntn Toyo Bearing Co Ltd | Double-row self-aligning roller bearing and device for supporting wind turbine generator main shaft |
| JP2005337267A (en) * | 2004-02-20 | 2005-12-08 | Mitsubishi Heavy Ind Ltd | Revolving wheel bearing structure for windmill |
| JP4533642B2 (en) * | 2004-02-20 | 2010-09-01 | 三菱重工業株式会社 | Winding wheel bearing structure for windmill |
| WO2006033320A1 (en) * | 2004-09-21 | 2006-03-30 | Ntn Corporation | Double-row self-aligning roller bearing and main shaft support structure for wind-turbine generator |
| US7922396B2 (en) | 2004-09-21 | 2011-04-12 | Ntn Corporation | Double row self-aligning roller bearing and main shaft support structure of wind power generator |
| JP2005147408A (en) * | 2005-01-11 | 2005-06-09 | Ntn Corp | Double row rolling bearing |
| JP4522266B2 (en) * | 2005-01-11 | 2010-08-11 | Ｎｔｎ株式会社 | Double row roller bearing |
| WO2006080127A1 (en) * | 2005-01-25 | 2006-08-03 | Ntn Corporation | Helical gear support structure, speed increaser for wind power generation plant, and vertical shaft support structure |
| US7927019B2 (en) | 2005-05-31 | 2011-04-19 | Mitsubishi Heavy Industries Ltd. | Slewing bearing structure |
| WO2007095953A1 (en) * | 2006-02-24 | 2007-08-30 | Vestas Wind Systems A/S | Gearbox for a wind turbine, bearing and method of manufacturing a bearing |
| CN102829076A (en) * | 2011-06-14 | 2012-12-19 | 瓦房店正达冶金轧机轴承有限公司 | Sealed four-row cylinder bearing |
| CN102619875A (en) * | 2012-04-10 | 2012-08-01 | 济南轨道交通装备有限责任公司 | Self-aligning roller bearing for main shaft of wind turbine generator and design method thereof |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2564261B2 (en) | 1996-12-18 |
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