JPS6039901B2 - Friction type shock absorber for transmission system - Google Patents
Friction type shock absorber for transmission systemInfo
- Publication number
- JPS6039901B2 JPS6039901B2 JP2616079A JP2616079A JPS6039901B2 JP S6039901 B2 JPS6039901 B2 JP S6039901B2 JP 2616079 A JP2616079 A JP 2616079A JP 2616079 A JP2616079 A JP 2616079A JP S6039901 B2 JPS6039901 B2 JP S6039901B2
- Authority
- JP
- Japan
- Prior art keywords
- cam
- lifter
- relay shaft
- friction
- driven
- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/129—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon characterised by friction-damping means
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
- Gears, Cams (AREA)
Description
【発明の詳細な説明】
本発明は、広範な負荷領域に亘り伝動系の換り振動を効
果的に減衰させるようにした摩擦式緩衝装置に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a friction damping device that effectively damps vibrations in a power transmission system over a wide range of loads.
従釆、伝動系の振り振動を減衰させるために、伝動系の
駆動および被動部材間に摩擦ダンパを介装することが知
られているが、従釆の摩擦ダンパは滑りトルクが一定で
あるため、擦り振動を有効に減衰し得る負荷領域が非常
に狭く、負荷領域の広い、例えば自動車の伝動系におい
ては所期の機能を充分に発揮し得ない欠点を有する。本
発明は上記にかんがみ、摩擦板式の摩擦クラッチの滑り
トルクが伝動系の受ける負荷の増大に応じて増大するよ
うにして、広範な負荷領域に亘り伝動系の換り振動を効
果的に減衰させることができ、しかもその摩擦クラッチ
のトルク負荷を軽減してその小容量化を達成し得るよう
にした構造簡単な摩擦式緩衝装置を提供することを目的
とし、その特徴は、被，駆動部村のいずれか一方に連動
する中継軸と、他方に運動して前記中継軸上に回転自在
に支承されるカムとの間に、その間のトルク伝動系路を
構成する第１および第２伝動機構を並列に介菱し、前記
第１伝導機構は、前記カムおよび中継軸の一方および他
方とそれぞれ回転方向に連結される駆動摩擦板および被
動摩擦板と、その両摩擦坂間を一体に回動するよう圧接
させるばねとより構成され、また前記第２伝動機構は、
前記中継軸上に相対回転不能且つ軸方向酒勤可能に支持
されて前記カムとばね間に介在するりフタより構成され
、前記カムは、それと前記リフタ間に相対回動が生じた
ときリフタに前記ばねの弾発力を増大させるスラストを
作用させ且つ該リフタとカム間でトルク伝達が直接なさ
れるようにリフタと係合するカム面を有してなる点にあ
る。It is known that a friction damper is interposed between the driving and driven members of the transmission system in order to damp vibrations in the transmission system, but since the sliding torque of the friction damper of the transmission system is constant, However, the load range in which rubbing vibrations can be effectively damped is very narrow, and the desired function cannot be fully exerted in a wide load range, such as an automobile power transmission system. In view of the above, the present invention allows the slipping torque of a friction plate type friction clutch to increase in accordance with the increase in the load applied to the transmission system, thereby effectively damping the displacement vibration of the transmission system over a wide range of load ranges. The purpose of the present invention is to provide a friction type shock absorber with a simple structure that can reduce the torque load on the friction clutch and achieve a small capacity. between a relay shaft interlocking with one of the relay shafts and a cam that moves in the other direction and is rotatably supported on the relay shaft, first and second transmission mechanisms constituting a torque transmission path therebetween are provided. The first transmission mechanism is arranged in parallel, and the first transmission mechanism rotates integrally between a driving friction plate and a driven friction plate, which are connected in the rotational direction to one and the other of the cam and the relay shaft, respectively, and between the two friction slopes. The second transmission mechanism is composed of a spring that is pressed into contact with the spring, and the second transmission mechanism is
The lid is supported on the relay shaft so as to be non-rotatable and axially movable, and is interposed between the cam and the spring, and the cam is configured to rotate the lifter when relative rotation occurs between the cam and the lifter. The cam surface has a cam surface that engages with the lifter so as to apply a thrust that increases the elastic force of the spring and to directly transmit torque between the lifter and the cam.
以下、図面により本発明の一実施例について説明すると
、図示例は自動二輪車における変速機Ｔの出力軸と後輪
駆動用の推進軸Ｐとの間を連結する中間伝動装置であっ
て、その伝動ケース１は変速機Ｔのケース後面に付設さ
れ、その内部に変速機Ｔの出力軸に連なる駆動スパーギ
ヤ２、それと噛合する被動スパーギャ３、それを左端部
で支承する中継軸４、その中継軸４の右端に蓮設した駆
動べベルギヤ５、それと噛合して推進軸Ｐを連結される
彼動べベルギャ６等が収容され、上記被動スパーギャ３
は、中継軸４上に回転自在に支承されていて、同じく中
継軸４上に回転自在に支承されるカム７とスプラィン結
合８されている。前記カム７は右端面に凹曲底面９ａを
もつＵ字状カム溝９を有する。このカム溝９には、中継
軸４に摺動自在にスプラィン結合１０するりフタ１１の
左端面に突設した作動脚１２が係合し、カム溝９と作動
脚１２との間にはカム７およびリフタ１１の一定の相対
回動を許容する間隙が設けられている。リフタ１１の右
端面からは内筒１３が一体に延出し、これを園績する外
筒１４がカム７の外周に摺動自在にスプラィン結合１６
される。Hereinafter, an embodiment of the present invention will be described with reference to the drawings. A case 1 is attached to the rear surface of the case of the transmission T, and inside thereof includes a driving spur gear 2 connected to the output shaft of the transmission T, a driven spur gear 3 meshing with the driving spur gear 2, a relay shaft 4 supporting it at the left end, and a relay shaft 4 for the driving spur gear 2 that meshes with the driving spur gear 2. A drive bevel gear 5 disposed at the right end of the drive bevel gear 5, a drive bevel gear 6 which meshes with the drive bevel gear 6 to connect the propulsion shaft P, etc. are accommodated, and the driven spur gear 3
is rotatably supported on the relay shaft 4, and is connected to a cam 7, which is also rotatably supported on the relay shaft 4, by a spline connection 8. The cam 7 has a U-shaped cam groove 9 with a concave bottom surface 9a on the right end surface. An operating leg 12 protruding from the left end surface of the slip cover 11 is engaged with the cam groove 9 so as to be slidable on the relay shaft 4, and a cam is connected between the cam groove 9 and the operating leg 12 A gap is provided to allow constant relative rotation of the lifter 7 and the lifter 11. An inner cylinder 13 integrally extends from the right end surface of the lifter 11, and an outer cylinder 14 that connects the inner cylinder 13 is slidably connected to the outer periphery of the cam 7 with a spline connection 16.
be done.
これら内，外筒１３，１４間には、それぞれ複数枚の駆
動摩擦板１６，１６・・・および被動摩擦板１７，１７
・・・を交互に重合した摩擦板群、この摩擦板群を左右
より被持する一対の披持板１８，１８′、および右側挟
持板１８′に隣接する押圧板１９が介装されるもので、
そのうち駆動摩擦板１６，１６・・・および挟持板１８
，１８′は外筒１４に左右の抜止環２０，２０′の間で
沼動自在にスプラィン結合２１３れ、そして左側挟持板
１８がリフタ１１の右端面に当接し、残る被動摩擦板１
７，１７・・・および押圧板１９は内筒１３に摺動自在
にスプラィン結合２２される。上記押圧板１９と、中継
軸４上の固定のばね座２３との間にはコイルばね２４が
所定のセット荷重を付与されて縞設される。而しては、
ぱね２４の弾発力は押圧板１９を介し侠持板１８，１８
′摩擦板１６，１７群、リフタ１１等をカム７に向って
弾発し、これにより駆動および被動摩擦板１６．１７間
に圧接力が付与され、それらの初期滑りトルクが設定さ
れる。而して前記両摩擦板１６，１７およびコイルばね
２４は本発明の第１伝動機構Ｄ，を、またリフ夕１ １
は同じく第２伝動機構Ｄ２をそれぞれ構成している。尚
、図中２５はカム７の抜止環、２６および２７は中継軸
４の両端部を支持するベアリング、２８および２９は被
動べベルギャ６を支持するベアリングである。Between these inner and outer cylinders 13 and 14, there are a plurality of driving friction plates 16, 16, and driven friction plates 17, 17, respectively.
..., a pair of supporting plates 18, 18' supporting this friction plate group from the left and right sides, and a pressing plate 19 adjacent to the right side holding plate 18' are interposed. in,
Of these, the driving friction plates 16, 16... and the clamping plate 18
, 18' are spline-coupled 213 to the outer cylinder 14 between the left and right retaining rings 20, 20' so as to be freely movable, and the left holding plate 18 abuts the right end surface of the lifter 11, and the remaining driven friction plate 1
7, 17, . . . and the press plate 19 are slidably spline-coupled 22 to the inner cylinder 13. A coil spring 24 is striped with a predetermined set load applied between the pressing plate 19 and a fixed spring seat 23 on the relay shaft 4. Therefore,
The elastic force of the spring 24 is applied to the holding plates 18, 18 via the pressing plate 19.
'The groups of friction plates 16 and 17, the lifter 11, etc. are ejected toward the cam 7, thereby applying a pressing force between the driving and driven friction plates 16 and 17, and setting their initial sliding torque. The friction plates 16, 17 and the coil spring 24 serve as the first transmission mechanism D of the present invention, and also as the lifter 1 1.
similarly constitute the second transmission mechanism D2. In the figure, 25 is a retaining ring for the cam 7, 26 and 27 are bearings that support both ends of the relay shaft 4, and 28 and 29 are bearings that support the driven bevel gear 6.
次にこの実施例の作用を説明する。Next, the operation of this embodiment will be explained.
図示しないエンジンが作動されると、その動力により変
速機Ｔを介して駆動スパーギャ２が所望の変速比で駆動
され、続いて駆動スパーギャ２より被動スパーギャ３が
それらのギャ比に応じて増速または減速駆動される。When the engine (not shown) is operated, the driving spur gear 2 is driven by the power through the transmission T at a desired gear ratio, and then the driving spur gear 2 causes the driven spur gear 3 to speed up or increase the speed according to the gear ratio. Driven by deceleration.
このとき、中継軸４にか）る負荷が両摩擦板１６，１７
の初期滑りトルク以下であれば、被動スパーギャ３の回
転トルクは、カム７、外筒１４、スプラィン結合部２１
、摩擦結合状態の駆動および被動摩擦板１６，１７、ス
プラィン結合２２を順次経て中継軸４に伝達し、さらに
一対のべベルギャ５，６、推進軸Ｐへと伝達して図示し
ない後輪を駆動する。At this time, the load on the relay shaft 4 is
If the initial sliding torque is less than the initial sliding torque of
, the drive in the frictionally coupled state is transmitted to the relay shaft 4 through the driven friction plates 16, 17 and the spline coupling 22 in order, and further transmitted to the pair of bevel gears 5, 6 and the propulsion shaft P to drive the rear wheels (not shown). do.
そして負荷が増大して両摩擦板１６，１７の初期滑りト
ルクを超えると、両摩擦板１６，１７間に滑りを生じて
カム７およびリフタ１１が相対的に回動し、リフタ１１
の作動軸１２がカム溝９の凹曲底面９ａを登るように滑
るため、リフタ１１は中継軸４上を右方へ摺敷して挟持
板１８，１８′、摩擦板１６，１７群、押圧板１９等を
ばね２４を圧縮するように押動する。When the load increases and exceeds the initial slipping torque of both friction plates 16 and 17, slippage occurs between both friction plates 16 and 17, causing cam 7 and lifter 11 to rotate relative to each other, causing lifter 11 to rotate relative to each other.
The operating shaft 12 slides up the concave curved bottom surface 9a of the cam groove 9, so the lifter 11 slides to the right on the relay shaft 4 and connects the clamping plates 18, 18', the groups of friction plates 16, 17, and the presser. The plate 19 and the like are pushed so as to compress the spring 24.
こうしてばね２４の弾発力を増加させることにより両摩
擦板１６，１７間の圧俵力、したがって滑りトルクの増
大を図ることができ、この結果、両摩擦板１６，１７に
負荷の増大に応じた滑り摩擦仕事をさせることができ、
負荷変動に起因した伝動系の模り振動を広い負荷領域に
亘って効果的に減衰し得る。また上記の如く、カム７お
よびリフタ１１が相対回動し、両摩擦板１６，１７の滑
りトルクが増加補正される間、カム７のカム面としての
カム溝９は、それとリフタ１１との係合力の回転方向分
力、すなわちカム７の回転トルクの一部をリフタ１１に
直接作用させることができるから、それだけ両摩擦板１
６，１７のトルク負担が軽減される。以上のように本発
明によれば、被，駆動部材のいずれか一方に連動する中
継職４と、他方に連動して前記中継軸４上に回転自在に
支承されるカム７との間に、その間のトルク伝動系路を
構成する第１および第２伝動機構Ｄ，，Ｄ２を並列に介
装し、前記第１伝動機構Ｐ，は、前記カム７および中継
軸４の一方および他方とそれぞれ回転方向に連結される
駆動摩擦板１６および被動摩擦板１７と、その両摩擦板
１６，１７間を一体に回動するよう圧接させるばね２４
とより構成され、また前記第２伝動機構Ｐ２は、前記中
継軸４上に相対回転不能且つ軸万向摺動可能に支持され
て前記カム７とばね２４間に介在するりフタ１１より構
成され、前記カム７は、それと前記リフタ１１間に相対
回動が生じたときリフタ１１に前記ばね２４の弾発力を
増大させるスラストを作用させ且つ譲りフタ１１とカム
７間でトルク伝達が直俊なされるようにリフタ１１と係
合するカム面を有しているので、伝動中、彼動部材の負
荷が増大して両摩擦板１６，１７の初期滑りトルクを超
えるようになると、両摩擦板１６，１７間が滑って前記
カム７とりフタ１１間に相対回動を生じさせ、この相対
回動に伴ない、前記カム７とＩＪフタ１１間でトルク伝
達が直接なされると共に前記ばね２４の弾発力が増大し
て両摩擦板１６，１７間の滑りトルクが増加補正され、
この結果、両摩擦板１６，１７に負荷の大きさに応じた
滑り摩擦仕事をさせることができ、低負荷から高負荷ま
での広い範囲に亘つて、負荷変動に起因した伝動系の操
り振動を効果的に減衰させることができ、伝動系各部の
破損を有効に防止し得る。In this way, by increasing the elastic force of the spring 24, it is possible to increase the pressure bale force between the two friction plates 16, 17, and therefore the sliding torque. It can do sliding friction work,
It is possible to effectively attenuate imitation vibrations in the transmission system caused by load fluctuations over a wide load range. Further, as described above, while the cam 7 and the lifter 11 rotate relative to each other and the sliding torque of both friction plates 16 and 17 is increased and corrected, the cam groove 9 as the cam surface of the cam 7 is in contact with the lifter 11. Since the rotational direction component of the resultant force, that is, a part of the rotational torque of the cam 7 can be directly applied to the lifter 11, both friction plates 1 can be
6 and 17 are reduced. As described above, according to the present invention, between the relay shaft 4 which is interlocked with one of the driven members and the cam 7 which is rotatably supported on the relay shaft 4 and which is interlocked with the other driven member, A first and a second transmission mechanism D, D2 that constitute a torque transmission system between them are interposed in parallel, and the first transmission mechanism P rotates with one and the other of the cam 7 and the relay shaft 4, respectively. A driving friction plate 16 and a driven friction plate 17 that are connected in the same direction, and a spring 24 that presses the two friction plates 16 and 17 so that they rotate together.
The second transmission mechanism P2 includes a lid 11 supported on the relay shaft 4 so as to be non-rotatable and slidable in all directions, and interposed between the cam 7 and the spring 24. When relative rotation occurs between the cam 7 and the lifter 11, the cam 7 acts on the lifter 11 with a thrust that increases the elastic force of the spring 24, and torque is directly transmitted between the lid 11 and the cam 7. Since it has a cam surface that engages with the lifter 11 so that the lifter 11 is engaged with the lifter 11 in a manner that , 17 to cause relative rotation between the cam 7 and the lid 11, and with this relative rotation, torque is directly transmitted between the cam 7 and the IJ lid 11, and the elasticity of the spring 24 is As the generated force increases, the sliding torque between both friction plates 16 and 17 is increased and corrected,
As a result, both friction plates 16 and 17 can perform sliding friction work in accordance with the magnitude of the load, and can suppress steering vibrations in the transmission system caused by load fluctuations over a wide range from low loads to high loads. Damping can be achieved effectively, and damage to various parts of the transmission system can be effectively prevented.
等に上記の如く、カム７及びリフタ１１が相対回動して
両摩擦板１６，１７間の滑りトルクが増加補正される間
は、駆，被動部村間のトルク伝達が前記第１伝動機構Ｄ
，のみならず、それと並列関係にある第２伝動機構Ｄ２
をも経由して行なわれるから、第１伝動機構Ｄ，を構成
する、両摩擦板１６，１７等よりなる摩擦クラッチのト
ルク負担を軽減して、その小容量化を達成することがで
き、装置のコストダウンおよび小型化に寄与し得る。し
かも前記カム７と協働して前記ばね２４の弾発力を増加
させるための前記リフタ１ １が、前記第２伝動機構Ｄ
２のトルク伝達部材にそのまま兼用されるので、第２伝
動機構Ｄ２の特設によるも構造は左程複雑にならず、コ
ストアップを抑えることができるものである。As mentioned above, while the cam 7 and the lifter 11 rotate relative to each other and the sliding torque between the friction plates 16 and 17 is increased and corrected, the torque transmission between the driving and driven parts is carried out by the first transmission mechanism. D
, as well as the second transmission mechanism D2 in parallel relationship with it.
Since the transmission is carried out via This can contribute to cost reduction and miniaturization. Moreover, the lifter 11, which cooperates with the cam 7 to increase the elastic force of the spring 24, is connected to the second transmission mechanism D.
Since it is used as the second torque transmission member as it is, the structure does not become so complicated even with the special installation of the second transmission mechanism D2, and an increase in cost can be suppressed.
第１剛ま本発明装置の一実施例を示す縦断面図、第２図
はその要部の側面図である。
○，，○２・・・・・・第１、第２伝動機構、Ｐ・・・
・・・被動部材としての推進軸、２・・・・・・駆動部
材としてのスパーギャ、４・・・・・・中継軸、７・・
…・カム、９・・・・．・カム面としてのカム溝、１１
……リフタ、１６……駆動摩擦板、１７・・・・・・被
動摩擦板、２４・・・・・・ばね。
第２図
第１図A vertical cross-sectional view showing an embodiment of the first rigid device of the present invention, and FIG. 2 is a side view of the main parts thereof. ○,,○2...First and second transmission mechanisms, P...
...propulsion shaft as a driven member, 2... spur gear as a driving member, 4... relay shaft, 7...
...・Cam, 9....・Cam groove as cam surface, 11
... Lifter, 16 ... Drive friction plate, 17 ... Driven friction plate, 24 ... Spring. Figure 2 Figure 1
Claims (1)
、他方に連動して前記中継軸４上に回転自在に支承され
るカム７との間に、その間のトルク伝動系路を構成する
第１および第２伝動機構Ｄ＿１，Ｄ＿２を並列に介装し
、前記第１伝動機構Ｄ＿１は、前記カム７および中継軸
４の一方および他方とそれぞれ回転方向に連動される駆
動摩擦板１６および被動摩擦板１７と、その両摩擦板１
６，１７間を一体に回動するよう圧接させるばね２４と
より構成され、また前記第２伝動機構Ｄ＿２は、前記中
継軸４上に相対回転不能且つ軸方向摺動可能に支持され
て前記カム７とばね２４間に介在するリフタ１１より構
成され、前記カム７は、それと前記リフタ１１間に相対
回動が生じたときリフタ１１に前記ばね２４の弾発力を
増大させるスラストを作用させ且つ該リフタ１１とカム
７間でトルク伝達が直接なされるようにリフタ１１と係
合するカム面を有してなる、伝動系の摩擦式緩衝装置。1. A torque transmission system is formed between a relay shaft 4 that interlocks with one of the driven and driven members and a cam 7 that interlocks with the other and is rotatably supported on the relay shaft 4. First and second transmission mechanisms D_1 and D_2 are interposed in parallel, and the first transmission mechanism D_1 has a driving friction plate 16 and a driven friction plate 16 which are interlocked in the rotational direction with one and the other of the cam 7 and the relay shaft 4, respectively. Dynamic friction plate 17 and both friction plates 1
The second transmission mechanism D_2 is supported on the relay shaft 4 so as to be non-rotatable and slidable in the axial direction, and the second transmission mechanism D_2 is supported on the relay shaft 4 so as to be non-rotatable and slidable in the axial direction. The cam 7 is composed of a lifter 11 interposed between the cam 7 and the spring 24, and the cam 7 applies a thrust to the lifter 11 that increases the elastic force of the spring 24 when relative rotation occurs between the cam 7 and the lifter 11. A friction type shock absorber for a transmission system, which has a cam surface that engages with the lifter 11 so that torque is directly transmitted between the lifter 11 and the cam 7.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2616079A JPS6039901B2 (en) | 1979-03-08 | 1979-03-08 | Friction type shock absorber for transmission system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2616079A JPS6039901B2 (en) | 1979-03-08 | 1979-03-08 | Friction type shock absorber for transmission system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS55119246A JPS55119246A (en) | 1980-09-12 |
| JPS6039901B2 true JPS6039901B2 (en) | 1985-09-07 |
Family
ID=12185792
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2616079A Expired JPS6039901B2 (en) | 1979-03-08 | 1979-03-08 | Friction type shock absorber for transmission system |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6039901B2 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5797938A (en) * | 1980-12-08 | 1982-06-17 | Honda Motor Co Ltd | Torsional vibration absorbing unit in drive system |
| JPS5874952A (en) * | 1981-10-29 | 1983-05-06 | Honda Motor Co Ltd | Supporting and sealing device of bearing for final driving shaft in speed change gear |
| JPS60157515A (en) * | 1984-01-27 | 1985-08-17 | Kawasaki Heavy Ind Ltd | Shock-absorbing device of power transmission mechanism |
| JPS6192332A (en) * | 1984-10-12 | 1986-05-10 | Kawasaki Heavy Ind Ltd | Damper unit for power transmission mechanism |
| EP0420392A3 (en) * | 1989-09-21 | 1993-03-03 | Dana Corporation | Transmission output assemly |
-
1979
- 1979-03-08 JP JP2616079A patent/JPS6039901B2/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS55119246A (en) | 1980-09-12 |
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