JPS5927447B2 - plain bearing - Google Patents
plain bearingInfo
- Publication number
- JPS5927447B2 JPS5927447B2 JP51011835A JP1183576A JPS5927447B2 JP S5927447 B2 JPS5927447 B2 JP S5927447B2 JP 51011835 A JP51011835 A JP 51011835A JP 1183576 A JP1183576 A JP 1183576A JP S5927447 B2 JPS5927447 B2 JP S5927447B2
- Authority
- JP
- Japan
- Prior art keywords
- flange
- shell
- groove
- end flange
- inner edge
- 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
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
- F16C43/00—Assembling bearings
- F16C43/02—Assembling sliding-contact 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
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
-
- 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
- F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
- F16C2226/50—Positive connections
- F16C2226/70—Positive connections with complementary interlocking parts
- F16C2226/76—Positive connections with complementary interlocking parts with tongue and groove or key and slot
-
- 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
- F16C2300/00—Application independent of particular apparatuses
- F16C2300/02—General use or purpose, i.e. no use, purpose, special adaptation or modification indicated or a wide variety of uses mentioned
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Sliding-Contact Bearings (AREA)
- Connection Of Plates (AREA)
Description
【発明の詳細な説明】
本発明は、部分円筒形のジャーナル外殼と、該外殼の一
方の、または両方の、軸方向端に配される、または近く
に配される別個の端フランジとを有する平軸受に関する
。DETAILED DESCRIPTION OF THE INVENTION The present invention has a partially cylindrical journal shell and a separate end flange disposed at or near the axial end of one or both of the shells. Regarding plain bearings.
そのような平軸受は、前記外殻におけるジャーナル荷重
と、前記フランジにおける端荷重を支持し得る。もし前
記外殼とフランジが、別々に製作されたのち、組立て間
または使用間における分離または転位を防止するための
充分な位置決めがそれらの間に確立されるように、相当
容易に互いに組立てられ得るならば便利である。外殻及
びフランジは、おのおの、多くの場合、鋼を以て成る強
じんな裏当部であつて、軸受材料、例えば、より軟かい
金属または塑性物質、を以て成るライニングを内張りさ
れたものを有する。Such plain bearings may support journal loads at the shell and end loads at the flange. If said shell and flange can be fabricated separately and then assembled together with relative ease so that sufficient positioning is established between them to prevent separation or dislocation during assembly or use. It's convenient. The shell and flange each have a strong backing, often of steel, lined with a lining of bearing material, such as a softer metal or plastic.
そのようなライニングは自動給油材料を以て成り得、そ
の結果として、使用間に潤滑流体を供給する必要が無い
ようにされ得、あるいはまた、軸受の寿命を持続させる
ように初めに充分な潤滑剤を供給することによつて、ま
たは連続的に、もしくは、時々、新たに潤滑剤を供給す
ることによつて、流体潤滑剤が使用され得る。本発明に
従えば、独立した端フランジは、該端に於ける、または
該端に近い、外殼の裏部に在ろ凹所に係合して、前記フ
ランジに在る２個以上の突起と前記外殼の２個以上の切
欠きに在る互いにＪ 共働する肩によつて円周方向に於
て位置決めされる。Such linings may be of self-lubricating material, so that there is no need to supply lubricating fluid between uses, or alternatively, there may be sufficient lubricant initially to sustain the life of the bearing. Fluid lubricants can be used by feeding or by feeding continuously or occasionally with fresh lubricant. According to the invention, a separate end flange engages in a recess in the back of the shell at or near said end and engages two or more projections on said flange. It is circumferentially positioned by cooperating shoulders in two or more notches of the shell.
前記凹所の側壁は軸方向に前記外殼に対して前記フラン
ジを位置決めするごとく働らき、もし軸方向位置決めが
両方の向きに要求されるならば、５ 前記凹所は、２個
の互いに軸方向に離された壁を有する前記外殻の裏部に
溝によつて構成され得る。The side walls of the recess serve to position the flange axially relative to the shell, and if axial positioning is required in both directions, 5 the recess serves to position the flange axially relative to the shell; It may be constituted by a groove on the back side of the shell with walls spaced apart.
同れにせよ、前記突起は好ましくは前記フランジから半
径方向内方へ突出していて、前記フランジが前記外殼に
対して完全に位置決めされうるように円周方向位置決め
を行う。薄い外殼によつて、該外殼を半径方向内方へ撓
曲したのち、それをはね戻らせて、前記凹所または溝を
前記フランジの半径方向内縁に係合させることによつて
、前記フランジと外殼とを組立てることが可能であるが
、前記外殼を撓曲させることが容易でない場合は、前記
突起、または各突起を前記フランジの平面から変形させ
、この間、前記フランジを前記溝に組立てたのち前記突
起または各突起を変形させてそれを円周方向位置決め場
所へ復させ、あるいは、前記外殼とフランジとを、前記
溝のすぐ外側に於て前記フランジの内縁によつて組立て
たのち、前記溝内へ圧入される局部部分に訃いて前記フ
ランジの内縁を変形させることも可能である。Regardless, the protrusion preferably projects radially inwardly from the flange and provides circumferential positioning so that the flange can be perfectly positioned relative to the shell. said flange by bending said shell radially inwardly with said thin shell and then springing said shell to engage said recess or groove with said radially inner edge of said flange. and an outer shell, but if it is not easy to bend the outer shell, the protrusion, or each protrusion, may be deformed from the plane of the flange, during which time the flange may be assembled into the groove. After the or each projection is deformed and returned to its circumferential position, or the shell and flange are assembled by the inner edge of the flange just outside the groove, the It is also possible to deform the inner edge of the flange due to the local portion being pressed into the groove.
前記局部部分は、材料が前記フランジの残部におけるよ
りも薄い潤滑溝に位置することが望ましい。本発明は各
種の形式を以て実施されうる。Preferably, said local portion is located in a lubricating groove where the material is thinner than in the remainder of said flange. The invention may be implemented in a variety of forms.
以下、添付図面を参照して実施例の若干を単に例示的に
説明する。第１図に示される本発明の平軸受は、半円筒
形の外殼１１と、１対の平らな半環形のフランジ１２と
を有する。Some embodiments will now be described, by way of example only, with reference to the accompanying drawings. The plain bearing of the present invention shown in FIG. 1 has a semi-cylindrical shell 11 and a pair of flat semi-annular flanges 12.
フランジ１２は外殼１１の各端に各１個配置されている
。これら構成要素は、おの卦の、裏当部を有し、該裏当
部は低摩擦軸受材料から成るライニングを有する。外殼
１１の中心に沿つて環形の潤滑用の溝１３が延在する。
溝１３は半径方向の通路１４を通じて潤滑剤を供給され
るように仕組まれている。各端に卦いてフランジ１２は
外殼１１の裏部に在る溝１５に係合し、組立ては、外殼
１１がフランジ１２の内縁１６内に嵌合するまで外殼１
１の端部を内方へ圧し曲げたのち、外殼１１のはね戻り
を許し以て第３図に示される如く、フランジ１２を溝１
５に半径方向に係合して位置された状態に保つことによ
つて達成される。One flange 12 is arranged at each end of the shell 11. Each of these components has a backing portion, the backing portion having a lining of low friction bearing material. An annular lubrication groove 13 extends along the center of the shell 11 .
The groove 13 is arranged to be supplied with lubricant through a radial passage 14. The flange 12 on each end engages a groove 15 on the back side of the shell 11, and assembly continues until the shell 11 fits within the inner edge 16 of the flange 12.
After pressing and bending the end of the flange 12 inward, the outer shell 11 is allowed to spring back and the flange 12 is inserted into the groove 1 as shown in FIG.
This is accomplished by radially engaging and holding the 5 in position.
第３図は、フランジ１２の裏当部の表面１７が溝１５の
一壁に対して軸方向に当接して位置されることを示して
いる。軸線方向外方の壁１８に当接して配置することも
、それが必要とされる用途に訃いて可能である。説明さ
れている実施例において、外殼１１の外殼１９と、フラ
ンジ１２の内縁１６は第３図に示される如く先細に形づ
くられている。フランジ１２の内縁は溝１５の底に位置
する。円周方向位置決めは、１対の半径方向内方に突出
した突起２２によつて行われる。該突起２２は、弦線２
４に沿つて肩２３を画成するフランジ１２の各円周方向
端部に各１個設けられている。外殼１１は、ノツチを形
づくるように切欠かれ、以て対応の係合肩を構成してい
る。フランジ１２の半径方向内縁１６を外殼１１の溝１
５に係合させるように、外殼１１を半径方向内方に変形
させるときは、その変形は、外殼１１の外表面がフラン
ジの突起２２の半径方向内縁を通り越え得るように十分
でなければならない。外殼１１がその定常位置にはね戻
るとき、前記肩は２３において係合して軸線方向、半径
方向及び円周方向に位置決めを完結することは理解され
るであろう。その直径に比し厚すぎるという理由によつ
て外殼１１を変形させることが不便である場合は、前記
突起２２は、第５図に示される３本の軸線２３の任意の
１本を中心として、折曲げられるように仕組まれ得る。FIG. 3 shows that the backing surface 17 of the flange 12 is positioned in axial abutment against one wall of the groove 15. FIG. An arrangement against the axially outer wall 18 is also possible depending on the application in which it is required. In the embodiment being described, the shell 19 of shell 11 and the inner edge 16 of flange 12 are tapered as shown in FIG. The inner edge of flange 12 is located at the bottom of groove 15. Circumferential positioning is provided by a pair of radially inwardly projecting projections 22. The protrusion 22 is connected to the string line 2
one at each circumferential end of the flange 12 defining a shoulder 23 along the flange 4; The outer shell 11 is cut out to form a notch, thereby forming a corresponding engagement shoulder. The radially inner edge 16 of the flange 12 is inserted into the groove 1 of the outer shell 11.
5, the deformation must be sufficient to allow the outer surface of the shell 11 to pass over the radially inner edge of the projection 22 of the flange. . It will be appreciated that when the shell 11 springs back to its home position, the shoulders engage at 23 to complete the axial, radial and circumferential positioning. If it is inconvenient to deform the shell 11 because it is too thick compared to its diameter, the protrusion 22 may be centered on any one of the three axes 23 shown in FIG. Can be designed to be folded.
折曲げは、それを容易に行い得るように前記フランジ１
２の一部を機械削りによつて除去したのちに行われる。
これによつて、前記突起２２は、前記フランジ１２が第
６図に卦いて矢印２４によつて図示される如き半径方向
運動によつて溝１５に係合されることを妨げず、前記突
起２２は、肩が２３に於て係合する迄、矢印２５によつ
て示される如く、フランジ１２の平面へ簡単に曲げ戻さ
れ得る。第５図及び第６図に示される軸受を組立てる一
代替方法においては、前記突起２２のただ１個がフラン
ジ１２の法平面から折曲げられる。The flange 1 is bent so that it can be easily bent.
This is done after removing a part of 2 by mechanical cutting.
Thereby, the projection 22 does not prevent the flange 12 from being engaged in the groove 15 by radial movement as illustrated by the arrow 24 in FIG. can be simply bent back into the plane of flange 12, as shown by arrow 25, until the shoulders are engaged at 23. In an alternative method of assembling the bearing shown in FIGS. 5 and 6, only one of the projections 22 is bent out of the normal plane of the flange 12.
該突起に訃いてフランジは、それが終端する点に対し１
８０て反対の点に卦いて円周方向運動を以て前記溝に挿
入され、次いで、前記フランジ１２は１８０の角度前記
溝に沿つて回転されたのち、前記突起は前記フランジの
平面へ曲げ戻され以て円周方向位置を確立する。フラン
ジが複数個の潤滑用の溝２７を形成される場合に特に適
する第７図、第８図及び第９図に示される修正形式に於
ては、フランジ１２の円周方向内縁の大部分は溝１５に
進入せず、外殼１１の背壁と同じ半径を有する。The flange attached to the protrusion is 1 point relative to the point where it terminates.
80 is inserted into the groove with a circumferential movement to the opposite point, and then the flange 12 is rotated along the groove through an angle of 180, after which the projection is bent back into the plane of the flange. to establish circumferential position. In the modification shown in FIGS. 7, 8 and 9, which is particularly suitable when the flange is formed with a plurality of lubrication grooves 27, a large portion of the circumferential inner edge of the flange 12 is It does not enter the groove 15 and has the same radius as the back wall of the shell 11.
それらが互いに対して正確に位置されるならば、潤滑溝
２７に卦けるフランジ１２の前記内縁の部分は第９図に
最も明らかに示される如く、金敷３１に対して軸線方向
に打込まれるたがね２９の使用によつて局部的に変形さ
れて溝１５内に押込まれる。第９図は、溝２７の切削後
に残つている材料３２はフランジの最大厚さよりも薄く
、従つて、変形はきわめて簡単であり、フランジ１２の
変形を生じさせないことを示している。実際上、金属は
３２に於て先細にされうる。第７〜９図に示された修正
形式に卦いては、フランジ１２の内縁の半径は外殼の背
部よりも小さくなく、突起２２上の肩２３は曲げを必要
とせず、簡単に適所に軸線方向に摺動されうるから、初
度組立ては簡単な軸方向運動によつて達成されることは
理解されるであろう。If they are positioned correctly with respect to each other, the portion of the inner edge of the flange 12 in the lubrication groove 27 will be driven axially against the anvil 31, as shown most clearly in FIG. By the use of the spring 29 it is locally deformed and forced into the groove 15. FIG. 9 shows that the material 32 remaining after cutting the groove 27 is thinner than the maximum thickness of the flange, and therefore deformation is very easy and does not result in deformation of the flange 12. In practice, the metal may be tapered at 32. In the modified form shown in Figures 7-9, the radius of the inner edge of flange 12 is no smaller than the back of the shell, and the shoulder 23 on projection 22 does not require bending and is easily axially moved into position. It will be appreciated that the initial assembly is accomplished by a simple axial movement, since the parts can be slid together.
第１図は本発明の一実施例の全搬配列を示した透視図：
第２図は第１図に示された軸受の端面図：第３図及び第
４図は、夫々、第２図の−線と−線とに沿つて取つた拡
大断面図；第５図は修正形式の軸受の、第２図に相当す
る図面；第６図は第５図の−線に沿つて取つた拡大断面
図；第７図はもう一つの修正形式の平軸受の第５図に相
当する図面；第８図は第７図の−線に沿つて切つた断面
図；第９図は第８図の拡大詳細図である。
図面上、１１は外殼、１２はフランジ、１３は溝、１４
は通路、１５は溝、１６は内縁、２２は突起、２３は肩
を夫々示す。FIG. 1 is a perspective view showing a full-carrier array according to an embodiment of the present invention:
FIG. 2 is an end view of the bearing shown in FIG. 1; FIGS. 3 and 4 are enlarged sectional views taken along lines - and -, respectively, in FIG. 2; FIG. 5 is an end view of the bearing shown in FIG. FIG. 6 is an enlarged sectional view taken along the line - in FIG. 5; FIG. 7 is a drawing corresponding to FIG. 5 of another modified type of plain bearing; Corresponding drawings: FIG. 8 is a cross-sectional view taken along the line -- in FIG. 7; FIG. 9 is an enlarged detail view of FIG. 8. In the drawing, 11 is the outer shell, 12 is the flange, 13 is the groove, and 14
15 is a channel, 16 is an inner edge, 22 is a protrusion, and 23 is a shoulder.
Claims (1)
または一端近くに、配された別個の端フランジとを有す
る平軸受にして、該端フランジがその２個以上の突起と
前記外殻の２個以上の切欠きとに在る互いに共働する肩
によつて円周方向に於て位置決めされるものにおいて、
前記突起は互いに円周方向に離れて配置され、前記各突
起の肩は前記端フランジのほぼ半径方向内方に向かつて
延び、前記端フランジの半径方向内方に在る内縁が、前
記外殻の裏部に在る円周方向に延びる凹所の軸方向に離
れた２個の側壁の間に係合し、もつて前記端フランジが
軸方向に位置決めされることを特徴とする平軸受。1. A partially cylindrical journal outer shell, and at one end of the outer shell,
or a plain bearing having a separate end flange disposed near one end, said end flange cooperating with two or more projections thereof and two or more notches in said shell; Positioned in the circumferential direction by
The protrusions are circumferentially spaced apart from each other, a shoulder of each protrusion extending generally radially inwardly of the end flange, and a radially inwardly inner edge of the end flange extending from the outer shell. A plain bearing, characterized in that it engages between two axially spaced side walls of a circumferentially extending recess on the back side of the bearing, such that the end flange is axially positioned.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB4849/75A GB1483011A (en) | 1975-02-05 | 1975-02-05 | Plain bearing |
| GB3814275 | 1975-09-17 | ||
| GB4211575 | 1975-10-15 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS51143155A JPS51143155A (en) | 1976-12-09 |
| JPS5927447B2 true JPS5927447B2 (en) | 1984-07-05 |
Family
ID=27254510
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP51011835A Expired JPS5927447B2 (en) | 1975-02-05 | 1976-02-05 | plain bearing |
Country Status (6)
| Country | Link |
|---|---|
| JP (1) | JPS5927447B2 (en) |
| AT (1) | AT345624B (en) |
| BR (1) | BR7600905A (en) |
| DE (1) | DE2604255C2 (en) |
| FR (1) | FR2300254A1 (en) |
| IT (1) | IT1053921B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH01104521U (en) * | 1988-01-04 | 1989-07-14 |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5662458U (en) * | 1979-10-22 | 1981-05-26 | ||
| IT1175166B (en) * | 1983-02-03 | 1987-07-01 | Clevite Srl | FLANGED HALF BEARING FOR ENGINEERING APPLICATIONS |
| FR2577449B1 (en) * | 1985-02-19 | 1988-11-25 | Coussinets Ste Indle | METHOD OF ASSEMBLING STOP FLANGES ON SMOOTH BEARING BY CRIMPING |
| IT1185794B (en) * | 1985-03-15 | 1987-11-18 | Trione & C Spa G | BUSH WITH THRUST BEARING AND PROCEDURE FOR ITS MANUFACTURE |
| FR2580747B1 (en) * | 1985-04-22 | 1991-09-06 | Federal Corp | COMPOSITE THRUST BEARING CONSISTING OF A RADIAL THRUST HAS AT LEAST ONE REPORTED AXIAL THRUST |
| AT387432B (en) * | 1987-07-06 | 1989-01-25 | Miba Gleitlager Ag | SLIDING BEARING |
| GB8721841D0 (en) * | 1987-09-17 | 1987-10-21 | Coussinets Ste Indle | Bearings |
| GB8829957D0 (en) * | 1988-12-22 | 1989-02-15 | Coussinets Ste Indle | Bearings |
| GB9004717D0 (en) * | 1990-03-02 | 1990-04-25 | Glacier Metal Co Ltd | Bearings |
Family Cites Families (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DD27427A (en) * | ||||
| FR514416A (en) * | 1919-05-01 | 1921-03-10 | Jules Joseph Alcide Chenu | Improvements made to bearing caps for low-strength metal bearings, in particular those for bearings formed in the end of partitions of partitioned aluminum housings |
| GB604196A (en) * | 1942-05-13 | 1948-06-30 | Gaston Georges Eugene Augereau | Improvements in or relating to bushes for bearings |
| DE874535C (en) * | 1943-08-20 | 1953-04-23 | Rudolf O Dipl-Ing Bracke | Composite bearing with collar rings and process for its manufacture |
| DE927779C (en) * | 1950-07-25 | 1955-05-16 | Hoeveler & Dieckhaus | Axle bearings for rail vehicles |
| US2737425A (en) * | 1953-03-27 | 1956-03-06 | Fisher W Reuen | Bearing liner |
| DE937499C (en) * | 1954-03-19 | 1956-01-05 | Werner Mertin | Built-in plain bearings |
| US2885532A (en) * | 1956-04-25 | 1959-05-05 | Borg Warner | Method of making pump bushings and the like |
| DE1030627B (en) * | 1956-10-10 | 1958-05-22 | Otto Scharlach Metallwerke | Plain bearings for small machines with high speeds, especially high-speed bicycle dynamo axles |
| SU139515A1 (en) * | 1960-05-30 | 1960-11-30 | Б.Л. Клаз | Detachable liner |
| GB1168914A (en) * | 1967-05-16 | 1969-10-29 | Glacier Co Ltd | Improvements in or relating to Bearings |
| GB1297559A (en) * | 1970-09-25 | 1972-11-22 | ||
| DE2108358A1 (en) * | 1971-02-22 | 1972-09-07 | Seifert W | Combination plain bearings |
| US3795428A (en) * | 1972-01-10 | 1974-03-05 | Caterpillar Tractor Co | Two-piece interlocked support/thrust bearings |
| GB1386253A (en) * | 1972-05-24 | 1975-03-05 | Vandervell Products Ltd | Flanged half bearings |
-
1976
- 1976-02-03 IT IT47934/76A patent/IT1053921B/en active
- 1976-02-04 DE DE2604255A patent/DE2604255C2/en not_active Expired
- 1976-02-04 BR BR7600905A patent/BR7600905A/en unknown
- 1976-02-05 FR FR7603161A patent/FR2300254A1/en active Granted
- 1976-02-05 JP JP51011835A patent/JPS5927447B2/en not_active Expired
- 1976-02-05 AT AT80976A patent/AT345624B/en not_active IP Right Cessation
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH01104521U (en) * | 1988-01-04 | 1989-07-14 |
Also Published As
| Publication number | Publication date |
|---|---|
| AT345624B (en) | 1978-09-25 |
| BR7600905A (en) | 1976-08-31 |
| IT1053921B (en) | 1981-10-10 |
| DE2604255A1 (en) | 1976-08-19 |
| ATA80976A (en) | 1978-01-15 |
| FR2300254B1 (en) | 1980-08-01 |
| FR2300254A1 (en) | 1976-09-03 |
| DE2604255C2 (en) | 1983-09-15 |
| JPS51143155A (en) | 1976-12-09 |
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