JPH089459Y2 - Rolling bearing for underrace lubrication - Google Patents

Rolling bearing for underrace lubrication

Info

Publication number
JPH089459Y2
JPH089459Y2 JP1989082000U JP8200089U JPH089459Y2 JP H089459 Y2 JPH089459 Y2 JP H089459Y2 JP 1989082000 U JP1989082000 U JP 1989082000U JP 8200089 U JP8200089 U JP 8200089U JP H089459 Y2 JPH089459 Y2 JP H089459Y2
Authority
JP
Japan
Prior art keywords
inner ring
cooling groove
rolling bearing
lubrication
underrace
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 - Lifetime
Application number
JP1989082000U
Other languages
Japanese (ja)
Other versions
JPH0320726U (en
Inventor
哲実 大森
昌平 中村
路芳 石丸
Original Assignee
エヌティエヌ株式会社
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 エヌティエヌ株式会社 filed Critical エヌティエヌ株式会社
Priority to JP1989082000U priority Critical patent/JPH089459Y2/en
Publication of JPH0320726U publication Critical patent/JPH0320726U/ja
Application granted granted Critical
Publication of JPH089459Y2 publication Critical patent/JPH089459Y2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6681—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
    • F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
    • F16C33/6677—Details of supply of the liquid to the bearing, e.g. passages or nozzles from radial inside, e.g. via a passage through the shaft and/or inner ring
    • 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
    • F16C37/00—Cooling of bearings
    • F16C37/007—Cooling of bearings of rolling 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
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls 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
    • 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
    • F16C19/24—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 radial load mainly
    • F16C19/26—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 radial load mainly with a single row of rollers

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)

Description

【考案の詳細な説明】 〔産業上の利用分野〕 この考案は、アンダーレース潤滑法を用いた転がり軸
受の改良構造に関する。DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention relates to an improved structure of a rolling bearing using an underlace lubrication method.

〔従来の技術〕 アンダーレース潤滑は、第６図に示すように、内輪の
軌道面下を通して潤滑油を供給し、内輪を冷却すると同
時に遠心力で軸受内に潤滑油を注ぎ込むようにした潤滑
法であって、特開昭61-96219号公報にこの潤滑法を用い
た高速円筒ころ軸受が記載されている。[Prior Art] Underrace lubrication is a lubrication method in which lubricating oil is supplied under the raceway surface of the inner ring to cool the inner ring and at the same time to pour the lubricating oil into the bearing by centrifugal force, as shown in FIG. However, Japanese Patent Application Laid-Open No. 61-96219 discloses a high speed cylindrical roller bearing using this lubrication method.

〔考案が解決しようとする課題〕[Problems to be solved by the device]

従来のアンダーレース潤滑用転がり軸受は、内輪冷却
用の溝を軸または内輪に直接設けていた。そのため、軸
と内輪との接触面積が減少するのでかなり大きなしめし
ろでもって嵌合する必要があり、圧入または引き抜きに
要する力が過大となるなど取り扱いが不便であった。し
かも、軸と内輪をそのように大きなしめしろで嵌合する
結果、冷却溝の形が内輪の軌道面に反映して軌道面の精
度に悪影響を及ぼすという問題がある。In the conventional rolling bearing for underrace lubrication, a groove for cooling the inner ring is provided directly on the shaft or the inner ring. Therefore, since the contact area between the shaft and the inner ring is reduced, it is necessary to fit the shaft with a considerably large interference, and the force required for press-fitting or pulling-out becomes excessive, which is inconvenient to handle. Moreover, as a result of fitting the shaft and the inner ring with such a large interference, there is a problem that the shape of the cooling groove is reflected on the raceway surface of the inner ring and adversely affects the accuracy of the raceway surface.

そこで、この考案は、述べたような従来のアンダーレ
ース潤滑用転がり軸受における問題点を解消せんとする
ものである。Therefore, this invention is intended to solve the problems in the conventional rolling bearing for underrace lubrication as described above.

〔課題を解決するための手段〕[Means for solving the problem]

この考案は、内輪を二体構造にすることによって上記
課題を解決した。すなわち、この考案のアンダーレース
潤滑用転がり軸受は、互いに嵌合した内側の第１内輪と
外側の第２内輪とからなり両者間に冷却溝を設けた内輪
を有している。This invention solves the above-mentioned problems by forming the inner ring into a two-body structure. That is, the rolling bearing for underrace lubrication according to the present invention has an inner ring which is composed of an inner first inner ring and an outer second inner ring which are fitted to each other and which has a cooling groove provided therebetween.

冷却溝は第１内輪の外周面または第２内輪の内周面の
どちらに形成させてもよい。The cooling groove may be formed on either the outer peripheral surface of the first inner ring or the inner peripheral surface of the second inner ring.

以下、添付図面に従って詳細に説明する。 Hereinafter, a detailed description will be given with reference to the accompanying drawings.

第１図において、アンダーレース潤滑用転がり軸受
は、回転軸（10）と嵌合する内輪（20）、図示しないハ
ウジングと嵌合する外輪（４）、これら内・外輪（20、
４）間に介在する転動体（６）、および、転動体（６）
を等間隔に保持する保持器（８）を含んでいる。なお、
アンギュラ玉軸受を例示したが、円筒ころ軸受その他の
周知のタイプの転がり軸受に適用することができる。In FIG. 1, a rolling bearing for underrace lubrication includes an inner ring (20) fitted to a rotating shaft (10), an outer ring (4) fitted to a housing (not shown), and inner and outer rings (20,
4) Rolling element (6) interposed between and rolling element (6)
Includes cages (8) for holding at equal intervals. In addition,
Although the angular ball bearing is exemplified, the present invention can be applied to cylindrical roller bearings and other well-known types of rolling bearings.

内輪（20）は互いに嵌合した第１内輪（22）と第２内
輪（24）とからなる二体構造であって、第１内輪（2
2）、第２内輪（24）との間に、円周方向等間隔に冷却
溝（26）を配設してある。各冷却溝（26）は内輪（20）
の一方の端面から他方の端面まで延在している。この冷
却溝（26）は、第２図に示すように第１内輪（22）の外
周面に形成させてもよいし、あるいは、第３図に示すよ
うに第２内輪（24）の内周面に形成させることもでき
る。The inner ring (20) has a two-body structure composed of a first inner ring (22) and a second inner ring (24) fitted to each other.
2) The cooling grooves (26) are arranged at equal intervals in the circumferential direction between the second inner ring (24) and the second inner ring (24). Each cooling groove (26) is an inner ring (20)
It extends from one end face to the other end face. The cooling groove (26) may be formed on the outer peripheral surface of the first inner ring (22) as shown in FIG. 2, or may be formed on the inner peripheral surface of the second inner ring (24) as shown in FIG. It can also be formed on the surface.

冷却溝（26）は、直線状、曲線状など任意の形状とす
ることができる。直線状の場合、例えば、軸線と平行
に、または、軸線に対して斜めに延在する。曲線状の場
合の例として、第２図および第３図は螺旋状に延在する
冷却溝（26）を示している。この場合、直線状のものに
比べて、潤滑油が内輪（20）の内部を流過するのに要す
る時間が長くなるため、冷却効果を高めるうえで有利で
ある。螺旋の向きは軸受の回転方向によって決まる。潤
滑油の流動抵抗を増大させない範囲で、螺旋状のほかに
も同様の効果を奏しうる適当な形状を採用することがで
きる。なお、冷却溝の断面形状についても、図面に例示
したものに限らず種々変更が可能である。The cooling groove (26) can have any shape such as a linear shape and a curved shape. In the case of a straight line, for example, it extends parallel to the axis or obliquely to the axis. As an example of a curved case, FIGS. 2 and 3 show a cooling groove (26) extending spirally. In this case, the time required for the lubricating oil to flow through the inside of the inner ring (20) becomes longer than that of the linear one, which is advantageous in enhancing the cooling effect. The direction of the spiral depends on the direction of rotation of the bearing. As long as the flow resistance of the lubricating oil is not increased, it is possible to adopt a suitable shape other than the spiral shape that can achieve the same effect. The cross-sectional shape of the cooling groove is not limited to the one illustrated in the drawings, and various changes can be made.

第２内輪（24）は、各冷却溝（26）から軌道溝に潤滑
油を導くための潤滑穴（28）を有する。また、第２内輪
（24）の軸方向の一端にスクープ（30）が一体に形成さ
れている。スクープ（30）と軸（10）との間には環状の
空所（32）が形成されており、この空所（32）はジェッ
トノズル（34）から噴射された潤滑油を受け入れて冷却
溝（26）に分配流入させる働きをする。The second inner ring (24) has a lubrication hole (28) for introducing lubricating oil from each cooling groove (26) to the raceway groove. Further, a scoop (30) is integrally formed at one axial end of the second inner ring (24). An annular space (32) is formed between the scoop (30) and the shaft (10), and the space (32) receives the lubricating oil injected from the jet nozzle (34) to cool the groove. It serves to distribute and flow into (26).

スクープ（30）は第４図に示すように内輪とは別体の
ものであってもよい。その場合、環状の空所（32）と冷
却溝（26）とを連通させるため、適当な数の通路（36）
と環状溝（38）をスクープ（30）に設ける。The scoop (30) may be separate from the inner ring as shown in FIG. In that case, an appropriate number of passages (36) are provided to connect the annular void (32) and the cooling groove (26).
And an annular groove (38) on the scoop (30).

〔作用〕[Action]

ジェットノズル（34）から噴射された潤滑油はスクー
プ（30）内の空所（32）に入り、ここから冷却溝（26）
に分岐・流入する。そして、内輪（20）の一方の端面か
ら他方の端面まで冷却溝（26）に沿って流過する潤滑油
によって内輪（20）が冷却される。潤滑油の一部は、遠
心力の作用で潤滑穴（28）から軸受内へ送り込まれる。
冷却溝（26）を出た潤滑油は排油穴（40）から排出され
る。The lubricating oil injected from the jet nozzle (34) enters the space (32) in the scoop (30), and from there, the cooling groove (26).
Branch into and flow into. Then, the inner ring (20) is cooled by the lubricating oil flowing along the cooling groove (26) from one end surface of the inner ring (20) to the other end surface thereof. A part of the lubricating oil is sent into the bearing through the lubricating hole (28) by the action of centrifugal force.
The lubricating oil that has flowed out of the cooling groove (26) is discharged from the oil drain hole (40).

〔考案の効果〕[Effect of device]

この考案によれば、内輪を二体構造にして第１内輪と
第２内輪との間に冷却溝を設けたことにより、冷却溝の
加工が容易となり、設計形状の自由度が増した。しか
も、直線状、曲線状など任意の形状を採用することがで
きるので、冷却溝の全長を長くして冷却効果の向上を図
ることができる。According to this invention, since the inner ring has a two-piece structure and the cooling groove is provided between the first inner ring and the second inner ring, the cooling groove is easily machined and the degree of freedom in designing is increased. Moreover, since an arbitrary shape such as a linear shape or a curved shape can be adopted, it is possible to increase the total length of the cooling groove and improve the cooling effect.

従来のように回転軸とのはめあい面にではなく第１内
輪と第２内輪の間に冷却溝を設けたので、両者を嵌合さ
せた状態で第２内輪の転走面に仕上げ加工を施すことが
できる。したがって、従来の一体ものの内輪の場合のよ
うに冷却溝の存在によって転走面が変形して精度が低下
するといった問題はない。Since the cooling groove is provided between the first inner ring and the second inner ring instead of the fitting surface with the rotating shaft as in the conventional case, the rolling surface of the second inner ring is finished in the state where both are fitted. be able to. Therefore, unlike the case of the conventional one-piece inner ring, there is no problem that the rolling surface is deformed by the presence of the cooling groove and the accuracy is lowered.

また、回転軸と内輪との接触面積を減少させないの
で、回転軸とのしめしろを従来のように大きくする必要
がなく、圧入・引き抜き等の作業が容易である。Further, since the contact area between the rotary shaft and the inner ring is not reduced, it is not necessary to increase the interference with the rotary shaft as in the conventional case, and the work such as press fitting / pulling out is easy.

内輪を二体構造としたことにより、回転軸とのしめし
ろとは関係なく第２内輪を第１内輪に大きなしめしろで
嵌合させ、回転数が増加しても回転軸と第１内輪とのし
めしろが零にならないようにして軸受内のラジアルすき
まの急激な減少を抑えることができる。つまり、第１、
第２内輪間にしめしろがあると、見かけ上の内輪軌道溝
の膨張量を抑えることができるので、軸受に予圧をかけ
て使用することができる。この点につき第５図に従って
さらに説明すると、同図は横軸に回転数（×103rpm）、
縦軸に内輪軌道溝の膨張量をとり、内径100mmの軸受に
おける回転数と内輪膨張量の関係を表している。図中、
破線は初期しめしろを零とした従来の一体ものの内輪の
場合、実線は回転数n1でしめしろが零になるような従来
の一体ものの内輪の場合、そして一点鎖線は、この考案
による二体構造の内輪でしめしろが零にならないように
したものの場合をそれぞれ示す。この図からわかるよう
に、しめしろが無くなると内輪の膨張量が急に大きくな
り、ラジアルすきまが減少することになる。したがっ
て、第１、第２内輪間で大きなしめしろを確保できるこ
とは非常に有利である。Since the inner ring has a two-piece structure, the second inner ring is fitted to the first inner ring with a large interference regardless of the interference with the rotation shaft, and even if the rotation speed increases, the rotation shaft and the first inner ring It is possible to prevent the radial interference in the bearing from rapidly decreasing by preventing the interference amount from becoming zero. That is, the first,
If there is interference between the second inner ring, the apparent expansion amount of the inner ring raceway groove can be suppressed, so that the bearing can be used with a preload. This point will be further described with reference to FIG. 5. In the figure, the horizontal axis shows the rotation speed (× 10 3 rpm),
The vertical axis represents the expansion amount of the inner ring raceway groove, and the relationship between the rotational speed and the inner ring expansion amount in a bearing having an inner diameter of 100 mm is shown. In the figure,
The broken line is the case of a conventional one-piece inner ring with zero initial interference, the solid line is the case of a conventional one-piece inner ring with zero interference at the number of revolutions n 1 , and the dot-dash line is the two body The case of the inner ring of the structure where the interference is not zero is shown respectively. As can be seen from this figure, when the interference is eliminated, the expansion amount of the inner ring suddenly increases and the radial clearance decreases. Therefore, it is very advantageous that a large interference can be secured between the first and second inner rings.

尚、第１内輪に比重／縦弾性係数の小さい材質を使う
と、遠心力による内輪の膨張量を抑えることが出来、軸
受内のすきまが減少するのを抑え、高速回転する上で有
利となる。Use of a material having a small specific gravity / longitudinal elastic coefficient for the first inner ring can suppress the amount of expansion of the inner ring due to centrifugal force, prevent the clearance in the bearing from decreasing, and are advantageous for high speed rotation. .

【図面の簡単な説明】 第１図はこの考案の実施例を示す断面図、 第２図は第１内輪の部分斜視図、 第３図は第２内輪の部分斜視図、 第４図は別の実施例を示す断面図、 第５図は回転数と内輪膨張量の関係を示すグラフ、 第６図は従来の技術を示す断面図である。 20:内輪 22:第１内輪 24:第２内輪 26:冷却溝 28:潤滑穴 30:スクープBRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a sectional view showing an embodiment of the present invention, FIG. 2 is a partial perspective view of a first inner ring, FIG. 3 is a partial perspective view of a second inner ring, and FIG. FIG. 5 is a cross-sectional view showing the relationship between the rotational speed and the inner ring expansion amount, and FIG. 6 is a cross-sectional view showing a conventional technique. 20: Inner ring 22: First inner ring 24: Second inner ring 26: Cooling groove 28: Lubrication hole 30: Scoop

Claims (4)

【実用新案登録請求の範囲】[Scope of utility model registration request] 【請求項１】互いに嵌合した内側の第１内輪と外側の第
２内輪とからなり第１、第２内輪間に冷却溝を設けた内
輪を有するアンダーレース潤滑用転がり軸受。1. A rolling bearing for underrace lubrication, comprising an inner ring having an inner first inner ring and an outer second inner ring fitted to each other and having a cooling groove provided between the first and second inner rings. 【請求項２】第１内輪の外周面に冷却溝を形成させた請
求項１のアンダーレース潤滑用転がり軸受。2. A rolling bearing for underrace lubrication according to claim 1, wherein a cooling groove is formed on the outer peripheral surface of the first inner ring. 【請求項３】第２内輪の内周面に冷却溝を形成させた請
求項１のアンダーレース潤滑用転がり軸受。3. A rolling bearing for underrace lubrication according to claim 1, wherein a cooling groove is formed on the inner peripheral surface of the second inner ring. 【請求項４】冷却溝が螺旋状である請求項１または２の
アンダーレース潤滑用転がり軸受。4. The rolling bearing according to claim 1, wherein the cooling groove has a spiral shape.
JP1989082000U 1989-07-11 1989-07-11 Rolling bearing for underrace lubrication Expired - Lifetime JPH089459Y2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP1989082000U JPH089459Y2 (en) 1989-07-11 1989-07-11 Rolling bearing for underrace lubrication

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP1989082000U JPH089459Y2 (en) 1989-07-11 1989-07-11 Rolling bearing for underrace lubrication

Publications (2)

Publication Number Publication Date
JPH0320726U JPH0320726U (en) 1991-02-28
JPH089459Y2 true JPH089459Y2 (en) 1996-03-21

Family

ID=31628428

Family Applications (1)

Application Number Title Priority Date Filing Date
JP1989082000U Expired - Lifetime JPH089459Y2 (en) 1989-07-11 1989-07-11 Rolling bearing for underrace lubrication

Country Status (1)

Country Link
JP (1) JPH089459Y2 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AU2003900386A0 (en) * 2003-01-30 2003-02-13 Amcor Limited A baking tray
JP2007331795A (en) * 2006-06-15 2007-12-27 Toyo Aluminum Ekco Products Kk Packaging container
CN106224387B (en) * 2016-08-31 2019-09-06 洛阳轴承研究所有限公司 A kind of angular contact ball bearing
IT202300012615A1 (en) * 2023-06-19 2024-12-19 Skf Ab THIN SECTION BEARING UNIT

Also Published As

Publication number Publication date
JPH0320726U (en) 1991-02-28

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