JPS6323630Y2 - - Google Patents
Info
- Publication number
- JPS6323630Y2 JPS6323630Y2 JP16100283U JP16100283U JPS6323630Y2 JP S6323630 Y2 JPS6323630 Y2 JP S6323630Y2 JP 16100283 U JP16100283 U JP 16100283U JP 16100283 U JP16100283 U JP 16100283U JP S6323630 Y2 JPS6323630 Y2 JP S6323630Y2
- Authority
- JP
- Japan
- Prior art keywords
- friction
- power transmission
- endless
- belt
- coefficient
- 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
- 230000005540 biological transmission Effects 0.000 claims description 69
- 230000003746 surface roughness Effects 0.000 description 5
- 239000000463 material Substances 0.000 description 4
- 230000008094 contradictory effect Effects 0.000 description 3
- 230000002159 abnormal effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000001133 acceleration Effects 0.000 description 1
- 239000010425 asbestos Substances 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 239000002783 friction material Substances 0.000 description 1
- 238000010030 laminating Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 239000005011 phenolic resin Substances 0.000 description 1
- 230000002028 premature Effects 0.000 description 1
- 229910052895 riebeckite Inorganic materials 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
Landscapes
- Transmissions By Endless Flexible Members (AREA)
Description
【考案の詳細な説明】
〔技術分野〕
本考案は、自動車等車両の変速機として用いる
ことのできるベルト式無段変速機の動力伝達用無
端ベルトに関する。[Detailed Description of the Invention] [Technical Field] The present invention relates to an endless belt for power transmission in a belt-type continuously variable transmission that can be used as a transmission for vehicles such as automobiles.
自動車等車両の変速機として、最近、ベルト式
無段変速機が提案されている。例えば、特公昭55
−6783（特願昭46−22871）、特開昭57−29845（特
願昭56−94107）等がある。
Recently, belt-type continuously variable transmissions have been proposed as transmissions for vehicles such as automobiles. For example,
-6783 (Japanese Patent Application No. 1983-22871), Japanese Patent Application Laid-open No. 57-29845 (Japanese Patent Application No. 56-94107), etc.
従来提案されているベルト式無段変速機は、一
方の回転軸と他方の回転軸に、Ｖ字形断面の周溝
を有するプーリが設けられており、このプーリに
動力伝達用無端ベルトが掛け渡されて、プーリの
Ｖ字形断面の周溝の幅が変えられることにより、
一方の回転軸から他方の回転軸に回転動力が無段
階に変速されて、伝達されるようになつている。 Conventionally proposed belt-type continuously variable transmissions are equipped with pulleys having a circumferential groove with a V-shaped cross section on one rotating shaft and the other rotating shaft, and an endless belt for power transmission is wrapped around these pulleys. By changing the width of the circumferential groove of the V-shaped cross section of the pulley,
Rotational power is transmitted from one rotating shaft to the other rotating shaft in a stepless manner.
このベルト式無段変速機に使用される動力伝達
用無端ベルトは、無端キヤリアと動力伝達ブロツ
クとから形成されており、無端キヤリアは普通に
は帯状の複数個のフープが積層されて形成されて
おり、この無端キヤリアに複数個の動力伝達ブロ
ツクが数珠繋ぎに取付けられて形成されている。 The endless belt for power transmission used in this belt-type continuously variable transmission is formed from an endless carrier and a power transmission block, and the endless carrier is usually formed by laminating a plurality of band-shaped hoops. A plurality of power transmission blocks are attached to this endless carrier in a chain.
なお、動力伝達用無端ベルトの動力伝達ブロツ
クには、プーリのＶ字形断面の周溝と摩擦接触す
る摩擦面が両側に設けられており、この動力伝達
ブロツクの摩擦面とプーリの周溝の摩擦係合によ
り、動力伝達用無端ベルトによる動力伝達がおこ
なわれる。 The power transmission block of the endless belt for power transmission is provided with friction surfaces on both sides that come into frictional contact with the circumferential groove of the V-shaped cross section of the pulley, and the friction between the friction surface of the power transmission block and the circumferential groove of the pulley is Due to the engagement, power is transmitted by the endless belt for power transmission.
ところで、プーリの周溝と摩擦係合する動力伝
達ブロツクの摩擦面は、従来、すべて同一材質で
形成され、かつ、同一表面粗度で形成されていた
ため、動力伝達ブロツクのすべての摩擦面が同一
の摩擦係数となつていた。 By the way, all the friction surfaces of the power transmission block that frictionally engage with the circumferential groove of the pulley were conventionally made of the same material and had the same surface roughness, so all the friction surfaces of the power transmission block were the same. The coefficient of friction was .
そのため、この動力伝達ブロツクの摩擦係数が
低いときには、一般的に耐摩耗性が大きいため、
耐久性は良いが、動力伝達時に動力伝達用無端ベ
ルトとプーリの摩擦接触にスリツプを生じ、伝達
効率が低下するという不都合を生じる。 Therefore, when the friction coefficient of this power transmission block is low, it generally has high wear resistance, so
Although it has good durability, slips occur in the frictional contact between the endless belt for power transmission and the pulley during power transmission, resulting in a disadvantage that the transmission efficiency decreases.
一方、摩擦係数が高いときには、スリツプなく
動力伝達され、伝達効率は良くなるが、一般的に
耐摩耗性が小さくなるため、早期に摩擦面が摩耗
し、寿命が短いという不都合があり、また、摩擦
係数が高いことにより円滑な変速ができず、振動
または異音が発生するという不具合を生じること
がある。 On the other hand, when the coefficient of friction is high, power is transmitted without slipping and the transmission efficiency is improved, but the wear resistance is generally low, so the friction surface wears out early and has a short lifespan. Due to the high coefficient of friction, smooth gear shifting may not be possible, which may cause problems such as vibration or abnormal noise.
このように、摩擦面の摩擦係数がすべて同一の
場合には、摩擦係数の高低により伝達効率と耐久
性とは相反する特性となつているため、伝達効率
と耐久性の両者を満足させることはできなかつ
た。尤も、中間の摩擦係数のときには、両方の長
所を併せ持つが、それは、長所欠点の中間状態で
併せ持つものであり、伝達効率、耐久性の両者を
十分満足させるものではなかつた。 In this way, when the friction coefficients of all friction surfaces are the same, transmission efficiency and durability have contradictory characteristics depending on the level of the friction coefficient, so it is impossible to satisfy both transmission efficiency and durability. I couldn't do it. Of course, when the friction coefficient is intermediate, the advantages of both are combined, but this is an intermediate state between the advantages and disadvantages, and it does not fully satisfy both transmission efficiency and durability.
而して、本考案は、上述した従来の点に鑑みて
なされたものであつて、その目的とするところ
は、動力伝達ブロツクの摩擦面の摩擦係数を異な
らせることにより、相反する特性の伝達効率およ
び耐久性の両者とも十分満足し得るものとするこ
とにある。
The present invention has been developed in view of the above-mentioned conventional points, and its purpose is to transmit contradictory characteristics by varying the friction coefficients of the friction surfaces of the power transmission block. The objective is to provide a product that satisfies both efficiency and durability.
この目的を達成する本考案の構成は、次の通り
である。
The configuration of the present invention that achieves this objective is as follows.
すなわち、上述した従来の一般的な動力伝達用
無端ベルトにおいて、摩擦面の摩擦係数が異なる
動力伝達ブロツクを少なくとも二種類設け、この
異なる摩擦面を有する動力伝達ブロツクの組合せ
を、数珠繋ぎ方向に繰り返して配列して、動力伝
達用無端ベルトを構成するものである。 That is, in the conventional general endless belt for power transmission described above, at least two types of power transmission blocks with different friction coefficients of friction surfaces are provided, and combinations of power transmission blocks having different friction surfaces are repeated in a daisy chain direction. When arranged, they constitute an endless belt for power transmission.
なお、この構成における動力伝達ブロツクの摩
擦面の摩擦係数を異ならせる実施態様としては、
摩擦面の材質を異ならせて摩擦係数を異ならせる
態様、同一の材質でも摩擦面の表面粗度を変える
ことにより摩擦係数を異ならせる態様、および、
この両者を組合せて摩擦係数を異ならせる態様、
等がある。 In addition, as an embodiment in which the friction coefficient of the friction surface of the power transmission block in this configuration is different,
A mode in which the coefficient of friction is varied by changing the material of the friction surface, a mode in which the coefficient of friction is varied by changing the surface roughness of the friction surface even if the material is the same, and
A mode in which the coefficient of friction is made different by combining these two,
etc.
また、上記構成における動力伝達ブロツクの組
合せの実施態様としては、異なる摩擦係数の摩擦
面のみを組合せた態様、異なる摩擦係数の摩擦面
のうち一種類は少なくとも複数個用いて組合せた
態様、等がある。 Examples of combinations of power transmission blocks in the above configuration include a combination of only friction surfaces with different friction coefficients, a combination of at least a plurality of one type of friction surfaces with different friction coefficients, etc. be.
本考案は、異なる摩擦係数に形成された動力伝
達ブロツクの摩擦面のうち、摩擦係数の高い摩擦
面により、プーリの周溝との十分な摩擦接触が得
られて、スリツプを生じさせることなく回転動力
を伝達することができ、十分な伝達効率を得るこ
とができる。
In this invention, among the friction surfaces of the power transmission block formed with different friction coefficients, the friction surface with a high friction coefficient can obtain sufficient frictional contact with the circumferential groove of the pulley and rotate without causing slip. Power can be transmitted and sufficient transmission efficiency can be obtained.
そして、異なる摩擦係数に形成された動力伝達
ブロツクの摩擦面のうち、摩擦係数の低い摩擦面
により、耐摩耗性が大きくされ、その結果、耐久
性を向上させることができ、動力伝達用無端ベル
トの寿命を向上させることができる。 Among the friction surfaces of the power transmission block formed with different friction coefficients, the friction surface with a low friction coefficient increases the wear resistance, and as a result, the durability can be improved, and the endless belt for power transmission can be improved. can improve the lifespan of
すなわち、単に摩擦係数の高い摩擦面のみをプ
ーリの周溝と摩擦接触させるときには、その摩擦
面の耐摩耗性は一般的に小さいため、摩擦面を早
期に摩耗させるが、本考案は動力伝達用無端ベル
トがプーリの周溝に掛け渡された状態で、異なる
摩擦係数の摩擦面が同時にプーリの周溝に摩擦係
合した状態にあるため、摩擦係数の高い摩擦面の
摩耗は、耐摩耗性の大きい摩擦係数の低い摩擦面
により保護されて、早期摩耗を防止することがで
きる。 In other words, when only the friction surface with a high friction coefficient is brought into frictional contact with the circumferential groove of the pulley, the wear resistance of that friction surface is generally low and the friction surface wears out prematurely. When the endless belt is stretched around the circumferential groove of the pulley, the friction surfaces with different friction coefficients are simultaneously in frictional engagement with the circumferential groove of the pulley. Protected by a low friction surface with a high coefficient of friction, premature wear can be prevented.
本考案の動力伝達用無端ベルトは、上述の様に
作用する結果、相反する特性の伝達効率と耐久性
の両者をともに十分なものにするという所期の目
的を達成することができる。
As a result of the endless belt for power transmission of the present invention functioning as described above, it is possible to achieve the intended purpose of achieving sufficient transmission efficiency and durability, which are contradictory characteristics.
また、本考案の動力伝達用無端ベルトは、動力
伝達時にスリツプしないことから、動力伝達ブロ
ツクの摩擦面およびプーリの周溝にスカツフイン
グが生じるのを防止することができる。 Furthermore, since the endless power transmission belt of the present invention does not slip during power transmission, scuffing can be prevented from occurring on the friction surface of the power transmission block and the circumferential groove of the pulley.
また、本考案の動力伝達ブロツクは摩擦係数の
高い摩擦面のみでないため、変速が円滑におこな
われ、振動および異音の発生を減少させることが
できるという効果も奏する。 Furthermore, since the power transmission block of the present invention does not consist of only friction surfaces with a high coefficient of friction, gear changes can be performed smoothly, and vibrations and abnormal noises can be reduced.
以下、本考案の実施例を図面に基づいて説明す
る。
Hereinafter, embodiments of the present invention will be described based on the drawings.
第１図ないし第３図は本考案の一実施例を示
す。第１図はベルト式無段変速機の基本的構成
図、第２図は動力伝達用無端ベルトがプーリに掛
け渡された状態の正面図、第３図は動力伝達ブロ
ツクが無端キヤリアに数珠繋ぎに支持された状態
の側面図を示す。 1 to 3 show an embodiment of the present invention. Figure 1 is a basic configuration diagram of a belt-type continuously variable transmission, Figure 2 is a front view of an endless power transmission belt wrapped around a pulley, and Figure 3 is a power transmission block connected to an endless carrier. Figure 3 shows a side view in a supported state.
第１図において、一方の回転軸１と他方の回転
軸２にはそれぞれプーリ３，４が設けられてお
り、この両プーリ３，４に動力伝達用無端ベルト
１０が掛け渡されて、回転動力が相互に伝達され
るようになつている。そして、動力伝達用無端ベ
ルト１０のプーリ３，４に掛け渡される位置が、
半径方向内方と外方の位置の間を変化することに
より、回転は無段変速されて伝達される。 In FIG. 1, pulleys 3 and 4 are provided on one rotating shaft 1 and the other rotating shaft 2, respectively, and an endless power transmission belt 10 is stretched around both pulleys 3 and 4 to generate rotational power. are now being transmitted to each other. The position where the endless power transmission belt 10 is stretched over the pulleys 3 and 4 is
By changing between radially inward and outward positions, rotation is transmitted in a continuously variable manner.
プーリ３，４は、第２図に示すように、一方が
固定プーリＡとされ、他方が可動プーリＢとされ
ており、かつ、この固定プーリＡと可動プーリＢ
の内側はＶ字形断面の周溝A1，B1が形成されて
おり、動力伝達用無端ベルト１０が摩擦係合する
ようになつている。 As shown in FIG. 2, one of the pulleys 3 and 4 is a fixed pulley A, and the other is a movable pulley B, and the fixed pulley A and the movable pulley B
Circumferential grooves A 1 and B 1 with a V-shaped cross section are formed on the inside of the belt, and the endless belt 10 for power transmission is frictionally engaged with the grooves A 1 and B 1 .
プーリ３，４は、可動プーリＢの軸方向移動に
よりその周溝A1，B1の軸方向幅は広くなつたり
狭くなつたり変化し、この周溝A1，B1に摩擦係
合する動力伝達用無端ベルト１０の位置が半径方
向内方と外方の位置の間を変動する。周溝A1，
B1間の幅が狭いときには動力伝達用無端ベルト
１０の位置は半径方向外方位置となり、幅が広い
ときには半径方向内方位置となる。 The axial width of the circumferential grooves A 1 and B 1 of the pulleys 3 and 4 changes by widening or narrowing as the movable pulley B moves in the axial direction. The position of the endless transmission belt 10 varies between radially inward and outward positions. Circumferential groove A 1 ,
When the width between B1 and B1 is narrow, the position of the endless power transmission belt 10 is radially outward, and when the width is wide, the position is radially inward.
動力伝達用無端ベルト１０は、第２図および第
３図に示すように、無端キヤリア１１と動力伝達
ブロツク１２とから構成されており、無端キヤリ
ア１１は、第３図に示すように、普通には金属で
形成された数枚のフープ１１ａ，１１ｂ，１１
ｃ，１１ｄが積層されて形成されている。 The endless belt 10 for power transmission is composed of an endless carrier 11 and a power transmission block 12, as shown in FIGS. 2 and 3, and the endless carrier 11 is, as shown in FIG. are several hoops 11a, 11b, 11 made of metal.
c and 11d are laminated.
動力伝達ブロツク１２は、第２図に示すよう
に、両側に無端キヤリア係合溝１３が形成されて
おり、この無端キヤリア係合溝１３により無端キ
ヤリア１１に支持されて取付けられる。この動力
伝達ブロツク１２は、第３図に示すように、複数
個の動力伝達ブロツク１１が互いに隣接するよう
に数珠繋ぎにされて取付けられている。また、動
力伝達ブロツク１２の両側部にはプーリ３，４の
周溝A1，B1と摩擦接触する摩擦面１４が設けら
れており、この摩擦面１４は周溝A1，B1のＶ字
形断面と略一致する傾斜面に形成されている。 As shown in FIG. 2, the power transmission block 12 has endless carrier engaging grooves 13 formed on both sides thereof, and is supported and attached to the endless carrier 11 by the endless carrier engaging grooves 13. As shown in FIG. 3, the power transmission blocks 12 are mounted in a daisy chain so that a plurality of power transmission blocks 11 are adjacent to each other. Further, on both sides of the power transmission block 12, there are provided friction surfaces 14 that make frictional contact with the circumferential grooves A 1 and B 1 of the pulleys 3 and 4 . It is formed into an inclined surface that substantially matches the cross section of the letter.
この動力伝達ブロツク１２の摩擦面１４は、第
３図に示すように、数珠繋ぎに配列された動力伝
達ブロツク１２において、異なる摩擦係数とされ
た摩擦面１４ａ，１４ｂが交互に組合せて配置さ
れている。摩擦面１４ａ，１４ｂの摩擦係数を異
ならせる具体例は、次の通りである。 As shown in FIG. 3, the friction surfaces 14 of the power transmission block 12 are arranged such that friction surfaces 14a and 14b having different friction coefficients are alternately arranged in the power transmission blocks 12 arranged in a chain. . A specific example of making the friction coefficients of the friction surfaces 14a and 14b different is as follows.
（具体例 １）
摩擦面１４ａ，１４ｂは同一材質で形成する
が、その表面粗度を変えることにより、摩擦係数
を異ならせる。例えば、摩擦面１４ａは研削のみ
をおこない、その表面粗さを3.2μRZ程度として、
比較的低い摩擦係数とするが、摩擦面１４ｂは研
削した面に更にシヨツトブラストをおこない、表
面を梨子地として、その表面粗さを25μRZ程度と
し、比較的高い摩擦係数とする。(Specific Example 1) The friction surfaces 14a and 14b are made of the same material, but the friction coefficients are made different by changing the surface roughness. For example, the friction surface 14a is only ground, and the surface roughness is set to about 3.2 μRZ.
Although the friction surface 14b has a relatively low coefficient of friction, the ground surface of the friction surface 14b is further shot blasted to give a pear-skinned surface with a surface roughness of about 25 μRZ, and a relatively high coefficient of friction.
（具体例 ２）
摩擦面１４ａ，１４ｂの材質を異ならせること
により、摩擦係数を異ならせる。例えば、摩擦面
１４ａは軸受鋼（JES SUJ2）により形成して、
比較的低い摩擦係数とするが、摩擦面１４ｂはア
スベスト等を基材としたフエノール樹脂等で結合
した摩擦材で形成して、比較的高い摩擦係数とす
る。(Specific Example 2) By making the friction surfaces 14a and 14b different from each other, the coefficient of friction is made different. For example, the friction surface 14a is formed of bearing steel (JES SUJ2),
The friction surface 14b has a relatively low coefficient of friction, but the friction surface 14b is made of a friction material made of asbestos or the like and bonded with phenol resin or the like, so as to have a relatively high coefficient of friction.
上記実施例は、摩擦係数の異なる摩擦面１４
ａ，１４ｂが交互に配設されているが、このうち
比較的高い摩擦係数の摩擦面１４ｂにより、動力
伝達用無端ベルト１０とプーリ３，４間の摩擦接
触がスリツプすることなくおこなわれ、効率よく
伝達される。 In the above embodiment, the friction surfaces 14 having different coefficients of friction
a and 14b are arranged alternately, and among these, the friction surface 14b with a relatively high friction coefficient allows frictional contact between the endless power transmission belt 10 and the pulleys 3 and 4 to occur without slipping, thereby increasing efficiency. Well communicated.
また、この摩擦係数の高い摩擦面１４は前後方
向に位置する比較的低い摩擦係数の摩擦面１４ａ
により保護されて、プーリ３，４のＶ字形断面の
周溝A1，B1への喰い込みが防止されるため、そ
の摩擦促進が防止され、耐久性をよくすることが
できる。 Moreover, this friction surface 14 with a high friction coefficient is a friction surface 14a with a relatively low friction coefficient located in the front-rear direction.
This prevents the V-shaped cross-sections of the pulleys 3 and 4 from biting into the circumferential grooves A 1 and B 1 , thereby preventing acceleration of friction and improving durability.
以上、本考案を図示した特定の実施例について
説明したが、本考案はかかる実施例に限定される
ものではなく、本考案の範囲内にて、その他種々
の実施例が可能なものである。 Although the present invention has been described above with reference to specific embodiments illustrated, the present invention is not limited to these embodiments, and various other embodiments are possible within the scope of the present invention.
例えば、前述の実施例は、異なる摩擦係数が二
種類の場合について説明したが、三種類あるいは
四種類であつてもよい。そして、この異なる摩擦
係数とされた摩擦面を適宜組合せて、繰り返し配
列すればよい。 For example, in the above-mentioned embodiment, the case where there are two types of different friction coefficients has been described, but there may be three or four types. Then, the friction surfaces having different friction coefficients may be appropriately combined and arranged repeatedly.
第１図ないし第３図は本考案の一実施例を示
し、第１図はベルト式無段変速機の基本的構成
図、第２図は動力伝達用無端ベルトがプーリに掛
け渡された状態を示す正面図、第３図は動力伝達
用無端ベルトの一部側面図である。
符号の説明 ３，４……プーリ、１０……動力
伝達用無端ベルト、１１……無端キヤリア、１２
……動力伝達ブロツク、１４，１４ａ，１４ｂ…
…摩擦面。
Figures 1 to 3 show one embodiment of the present invention, Figure 1 is a basic configuration diagram of a belt-type continuously variable transmission, and Figure 2 shows a state in which an endless belt for power transmission is stretched around a pulley. FIG. 3 is a partial side view of the endless belt for power transmission. Explanation of symbols 3, 4...Pulley, 10...Endless belt for power transmission, 11...Endless carrier, 12
...Power transmission block, 14, 14a, 14b...
...Friction surface.
Claims (1)
る摩擦面を有する複数個の動力伝達ブロツクが、
無端キヤリアに数珠繋ぎに支持されて形成された
動力伝達用無端ベルトにおいて、 摩擦面の摩擦係数が異なる動力伝達ブロツクが
少なくとも二種類設けられ、この異なる摩擦面を
有する動力伝達ブロツクの組合せが、数珠繋ぎ方
向に繰り返し配列されていることを特徴とする動
力伝達用無端ベルト。[Claims for Utility Model Registration] A plurality of power transmission blocks each having a friction surface that makes frictional contact with a pulley having a circumferential groove having a V-shaped cross section,
In an endless belt for power transmission formed by being supported in a chain on an endless carrier, at least two types of power transmission blocks with different friction coefficients of friction surfaces are provided, and a combination of power transmission blocks having different friction surfaces is arranged in a chain direction. An endless belt for power transmission characterized by repeatedly arranging.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16100283U JPS6067451U (en) | 1983-10-18 | 1983-10-18 | Endless belt for power transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16100283U JPS6067451U (en) | 1983-10-18 | 1983-10-18 | Endless belt for power transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6067451U JPS6067451U (en) | 1985-05-13 |
| JPS6323630Y2 true JPS6323630Y2 (en) | 1988-06-29 |
Family
ID=30353960
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP16100283U Granted JPS6067451U (en) | 1983-10-18 | 1983-10-18 | Endless belt for power transmission |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6067451U (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006038140A (en) * | 2004-07-28 | 2006-02-09 | Tsubakimoto Chain Co | Driving chain |
-
1983
- 1983-10-18 JP JP16100283U patent/JPS6067451U/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6067451U (en) | 1985-05-13 |
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