JPS59122702A - Total flow turbine device - Google Patents
Total flow turbine deviceInfo
- Publication number
- JPS59122702A JPS59122702A JP23021982A JP23021982A JPS59122702A JP S59122702 A JPS59122702 A JP S59122702A JP 23021982 A JP23021982 A JP 23021982A JP 23021982 A JP23021982 A JP 23021982A JP S59122702 A JPS59122702 A JP S59122702A
- Authority
- JP
- Japan
- Prior art keywords
- steam
- phase flow
- turbine
- separation drum
- hot water
- 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
- 230000005514 two-phase flow Effects 0.000 claims abstract description 45
- 238000000926 separation method Methods 0.000 claims abstract description 37
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 35
- 238000010248 power generation Methods 0.000 description 5
- 239000007788 liquid Substances 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000003068 static effect Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 2
- 238000010795 Steam Flooding Methods 0.000 description 1
- 238000007664 blowing Methods 0.000 description 1
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K21/00—Steam engine plants not otherwise provided for
- F01K21/005—Steam engine plants not otherwise provided for using mixtures of liquid and steam or evaporation of a liquid by expansion
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/32—Collecting of condensation water; Drainage ; Removing solid particles
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は二相流タービンの回転分離ドラムを設けた同一
のロータに蒸気タービンを組み込んタトータルフロータ
ービン装置に崗するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention is directed to a total flow turbine system in which a steam turbine is incorporated in the same rotor provided with a rotating separation drum of a two-phase flow turbine.
地熱発電のために地下より取出された高温高圧の熱水ま
たは二相流は、回転分離式二相流タービンの二相流ノズ
ルで膨張させることにより、高速二相流を形成した後、
その高速二相流を回転分離ドラムに吹きつけることによ
り、その高速二相流の持つ熱エネルギーが回転分離ドラ
ムを回転運動させる動力に変換させることができること
は、反動タービンに関する特開昭５６−１５４１０２号
の発明等により公知である。High-temperature, high-pressure hot water or two-phase flow extracted from underground for geothermal power generation is expanded in a two-phase flow nozzle of a rotary separation type two-phase flow turbine to form a high-speed two-phase flow.
By blowing the high-speed two-phase flow onto the rotary separation drum, the thermal energy of the high-speed two-phase flow can be converted into power for rotating the rotary separation drum. It is well known from the invention of No.
即ち、回転分離ドラムは高速回転しており、二相流ノズ
ルから出た高速二相流は遠心分離され、熱水は回転分離
ドラム内に回転液面を作り、高速二相流が直接回転分離
ドラムＧこ当るのを防止すると共に、回転分離ドラムの
回転運動動力として伝達される。That is, the rotary separation drum rotates at high speed, the high-speed two-phase flow coming out of the two-phase flow nozzle is centrifugally separated, the hot water creates a rotating liquid surface in the rotary separation drum, and the high-speed two-phase flow is directly rotated and separated. This prevents the drum G from hitting and is transmitted as the rotational motion power of the rotating separation drum.
一方、遠心分離された蒸気は別置された蒸気タービンを
駆動して、その熱エネルギーを運動エネルギーＯこ変換
するようＱこなっている。On the other hand, the centrifuged steam drives a separately placed steam turbine to convert its thermal energy into kinetic energy.
また、回転分離ドラムの回転液面は、その熱水の粘性抵
抗で回転分離ドラムに動力を伝達すると共に、その回転
液面内に開口するディフューザを設ければ、ディフュー
ザが回転液面内の熱水を吸い取る作用をすることにより
、ディフューザ（こより、動圧を静圧に変換して昇圧し
熱水を送り出すポンプ動力ともなることが知られている
。In addition, the rotating liquid level of the rotating separating drum transmits power to the rotating separating drum through the viscous resistance of the hot water, and if a diffuser is provided that opens into the rotating liquid level, the diffuser can absorb the heat within the rotating liquid level. It is known that by absorbing water, a diffuser converts dynamic pressure into static pressure, increases the pressure, and serves as a pump power to send out hot water.
しかしながら、第１図Ｇこ示すごとく、従来の回転分離
式の二相流タービン１は、二相流ＷＳから分離された蒸
気Ｓの潜熱を利用する機能を持たず、二相流ノズルで膨
張され回転分離ドラムで分離された蒸気Ｓを別置された
蒸気タービン２に供給する方式を取っており、独立した
２種類のタービンを必要とし、タービン本体のみならず
、その給油装置などの補機も２種類必要であり、コスト
高（こなるという欠点があり、更にそれらの制御も複雑
Ｇこなるという欠点がある。However, as shown in Fig. 1G, the conventional rotary separation type two-phase flow turbine 1 does not have the function of utilizing the latent heat of the steam S separated from the two-phase flow WS, and the steam S is expanded by the two-phase flow nozzle. The system uses a system in which steam S separated by a rotating separation drum is supplied to a separately installed steam turbine 2, which requires two independent turbines, and not only the turbine itself but also auxiliary equipment such as its oil supply system. Two types are required, which has the drawback of high cost, and furthermore, the control thereof is complicated.
なお、第１図で３で示すのは全電気で、４で示すのは復
水器、そしてＷは熱水を示している。In Fig. 1, 3 indicates all electricity, 4 indicates a condenser, and W indicates hot water.
そこで本発明は、前記従来の欠点を解消するためになさ
れたものであり、回転分離ドラムの外周に蒸気タービン
の翼を設けることにより、二相流ノズル出口の二相流速
度及び蒸気ノズル出口の蒸気速度の各々の回転方向角速
度を同一にすることができることＧこ着目し、従来の二
相流タービンと蒸気タービンとを一体化してその熱サイ
クル効率の向上をはかると共に、フン・ゼクトで全体コ
ストの安いトータルフロータ−ビン装置を提供すること
を目的としたものである。The present invention has been made to solve the above-mentioned conventional drawbacks, and by providing steam turbine blades on the outer periphery of the rotating separation drum, the two-phase flow velocity at the two-phase flow nozzle outlet and the two-phase flow velocity at the steam nozzle outlet are improved. Focusing on the fact that the angular velocity in each rotational direction of the steam velocity can be made the same, we integrated a conventional two-phase flow turbine and a steam turbine to improve their thermal cycle efficiency, and at the same time, reduced the overall cost. The purpose of this invention is to provide an inexpensive total flow turbine device.
即ち本発明のトータルフロータ−ビン装置は、熱水また
は二相流を二相流ノズルから膨張させて高速二相流を形
成し、その高速二相流をロータに設けた回転分離ドラム
にて蒸気と熱水とに分離させる二相流タービンにおいて
、分離された蒸気の熱エネルギーを該回転分離ドラムの
外周に設けられた蒸気タービン（こより動力に変換可能
とすると共Ｇこ、分離された熱水の熱エネルギーをその
熱水が該回転分離ドラムからディフューザ部経由排出さ
れる際に動力に変換可能としたことを特徴としたもので
ある。That is, the total flow turbine device of the present invention expands hot water or a two-phase flow from a two-phase flow nozzle to form a high-speed two-phase flow, and converts the high-speed two-phase flow into steam in a rotating separation drum provided with a rotor. In a two-phase flow turbine that separates steam and hot water, the thermal energy of the separated steam can be converted into power by a steam turbine installed on the outer periphery of the rotating separation drum. The present invention is characterized in that the thermal energy of the hot water can be converted into power when the hot water is discharged from the rotating separation drum via the diffuser section.
以下図面を参照して本発明の詳細な説明するが、第２図
は本発明の実施例１におけるトータルフロータ−ビン装
置の概略側断面図であり、第３図は第２図の系統図であ
り、第１図と同じ、。The present invention will be described in detail below with reference to the drawings. Fig. 2 is a schematic side sectional view of a total flow turbine device in Embodiment 1 of the present invention, and Fig. 3 is a system diagram of Fig. 2. Yes, same as Figure 1.
部品は同じ部品番号で示している。Parts are designated by the same part number.
まず、このトータルフロータ−ビン５Ｇこは、第２図（
こ示すごとく圧力Ｐｌの高圧の熱水または二相流ＷＳが
入り、二相流ノズル６から圧力Ｐ２．こ膨張されて高速
二相流を形成し、その高速二相流が軸受７Ｇこより支持
された回転軸８Ｇこ固設されたロータ９の外周に設けら
れた回転分離ドラム１０にて、蒸気Ｓと熱水Ｗとに気水
分離されるようになっている。First, this total flow turbine 5G is shown in Figure 2 (
As shown, high-pressure hot water or two-phase flow WS of pressure Pl enters, and pressure P2. This is expanded to form a high-speed two-phase flow, and the high-speed two-phase flow is separated into steam S and Steam and water are separated into hot water W.
そこで、上記のごとく分離された熱水Ｗは、この回転分
離ドラム１０により減速されてロータ９の軸動カーに変
換され、更（こその回転分離ドラム１０内の熱水Ｗは、
その回転分離ドラム１０内に端部を開口したディフュー
ザＩＮこよりその動圧が高圧の静圧に変換されて昇圧さ
れ、動力Ｅ３相当のポンプ機能をはだすことＧこなる。Therefore, the hot water W separated as described above is decelerated by this rotating separation drum 10 and converted into an axially moving car of the rotor 9, and furthermore, the hot water W in the rotating separation drum 10 is
Through the diffuser IN, which has an open end inside the rotating separation drum 10, the dynamic pressure is converted to high static pressure and boosted, thereby providing a pumping function equivalent to the power E3.
ここで、二相流ノズル６出口の二相流速度を■とすると
、回転分離ドラム１０の周速を’−ｒＶに減速した場合
が最大軸動力Ｅ２が発生する。Here, assuming that the two-phase flow velocity at the outlet of the two-phase flow nozzle 6 is (■), the maximum shaft power E2 is generated when the circumferential speed of the rotary separation drum 10 is decelerated to '-rV.
また、回転分離ドラム１０内の熱水Ｗは、この場合、１
■の速度エネルギーを持っており、これをディフューザ
ー１によりすくい取ることＧこより動圧を静圧に変換し
、高圧を得ることができる。Moreover, in this case, the hot water W in the rotating separation drum 10 is 1
It has a velocity energy of (2), and by scooping it up with the diffuser 1 (G), it is possible to convert dynamic pressure into static pressure and obtain high pressure.
一方、回転分離ドラムＩＯＧこて気水分離された蒸気Ｓ
は、その回転分離ドラム１０の外周Ｇこ設けられた蒸気
タービン１２のノズル１２Ａ及び回転羽根１２Ｂ部分で
圧力Ｐ３に膨張し、その熱エネルギーは軸動力ＥＩＧこ
変換され、回転分離ドラム１０と同一の回転軸８の軸動
力となる。On the other hand, the rotating separation drum IOG trowel steam and water separated steam S
is expanded to a pressure P3 at the nozzle 12A and rotary blade 12B of the steam turbine 12 provided on the outer periphery of the rotating separation drum 10, and the thermal energy is converted to the shaft power EIG, which is the same as the rotating separation drum 10. This becomes the shaft power of the rotating shaft 8.
このことは、一般に蒸気タービン１２のノズル１２Ａの
出口蒸気の速度は、回転分離ドラム１０の速度よりも高
速であるから、蒸気タービン１２の回転羽根１２Ｂを回
転分離ドラム１０の外周Ｇこ設置することＧこより、周
方向の角速度を同−Ｇこできることに着目したものであ
る。This means that since the speed of steam at the outlet of the nozzle 12A of the steam turbine 12 is generally higher than the speed of the rotary separation drum 10, it is necessary to install the rotary blades 12B of the steam turbine 12 on the outer periphery of the rotary separation drum 10. This is because the angular velocity in the circumferential direction can be increased by -G.
以上の構成からなる本発明のトータルフロータービン５
では、同一のロータ９に回転分離ドラム１０と蒸気ター
ビン１２とが組み込まれているので、第１図の従来例に
示した二相流タービン１と蒸気タービン２とが、第３図
に示すごとく一体Ｇこなっており、このトータルフロー
タ−ビン５においては、圧力Ｐｌの熱水または二相流Ｗ
Ｓの持つ熱エネルギーはＥｌ ＋ Ｅｚ ＋ Ｅ３相当
の動力に変換されることになる。Total flow turbine 5 of the present invention having the above configuration
Now, since the rotary separation drum 10 and the steam turbine 12 are incorporated into the same rotor 9, the two-phase flow turbine 1 and the steam turbine 2 shown in the conventional example of FIG. In this total flow turbine 5, hot water at pressure Pl or two-phase flow W
The thermal energy possessed by S will be converted into power equivalent to El + Ez + E3.
次に、第４図は本発明の実施例２におけるトータルフロ
ータ−ビン装置の概略側断面図であり、第２図と同じ部
品は同じ部品番号で示しており、実施例１とほぼ同様の
機能を有するものであるが、この実施例２では、ロータ
９に設けられた回転分離ドラム１０内の熱水Ｗの運動エ
ネルギーをディフューザ１１経由排出する際に、回転軸
８の外周に回転自在に設けられた回転軸１３に設けられ
たペルトン型の水車１４にて取り出すようにしたもので
ある。Next, FIG. 4 is a schematic side sectional view of a total flow turbine device according to a second embodiment of the present invention, in which the same parts as in FIG. 2 are indicated by the same part numbers, and the functions are almost the same as in the first embodiment. However, in this second embodiment, when discharging the kinetic energy of the hot water W in the rotating separation drum 10 provided on the rotor 9 via the diffuser 11, a The water is taken out by a Pelton type water wheel 14 provided on a rotary shaft 13.
この場合、回転分離ドラム１０は二相流ノズル６出日の
二相流速度■とほぼ同じ周速で回転し、れる。In this case, the rotary separation drum 10 rotates at approximately the same circumferential speed as the two-phase flow velocity (2) of the two-phase flow nozzle 6.
ただし、−！−■で回転する場合には、水車１４の機能
はなくなる。However, -! -■ When rotating, the function of the water wheel 14 is lost.
即ち、本実施例２のごとく波ルトン型の水車１４を採用
する場合には、ポンプ動力は重視せず、軸動力を最大化
することが目的である、。That is, when adopting the Wavelton type water turbine 14 as in the second embodiment, the purpose is to maximize the shaft power without placing emphasis on the pump power.
水車１４の回転速度は、回転分離ドラム１０の回転速度
の約１であるので、水車１４ と回転分離ドラム１０
の間には、約２倍の増速用の歯車装置１５を用いること
により、ロータ９の回転軸８と水車１４の回転軸１３と
を一体Ｇこして回転することができる。Since the rotational speed of the waterwheel 14 is approximately 1 that of the rotational separation drum 10, the rotational speed of the waterwheel 14 and the rotational separation drum 10 are
In between, by using a gear device 15 for increasing the speed by about twice as much, the rotating shaft 8 of the rotor 9 and the rotating shaft 13 of the water wheel 14 can be rotated integrally by G.
従って、本発明のトータルフロータ−ビン装置は、高圧
高温の熱水、または二相流体の膨張器、気水分離装置、
二相流ター２ン、蒸気タービンの機能を併せ持つ画期的
な単一のタービン装置であり、構造が簡単で、かつコン
パクトであり、地熱発電プラレトに採用した場合、その
プラントを簡単にし、また熱サイクル効率も良いので、
発電単価を安くできるという効果力；あＩる。Therefore, the total flow turbine device of the present invention includes a high-pressure and high-temperature hot water or two-phase fluid expander, a steam-water separation device,
It is a revolutionary single turbine device that combines the functions of a two-phase flow turbine and a steam turbine.It has a simple and compact structure, and when adopted in a geothermal power generation plant, it will simplify the plant. It has good heat cycle efficiency, so
The effectiveness of lowering the unit cost of power generation;
また、大半の地熱井は熱水卓越型であるカニ、本発明の
トータルフロータ−ビン＋ｔ、従来の蒸気タービン方式
とは異なり、熱水の持つ顕熱も利用することができ、し
かも蒸気タービンσ）機能も併せ持っているので、蒸気
潜熱をも第１１用できるので、二相流ノズル出口圧を余
り低圧Ｇこしなくても蒸気タービン方式や、他の二相流
タービンのみの方式よりも効率が良く、還元井へσ〕湿
温度下げなくて済み、スケール付着の防止（こなる。In addition, most geothermal wells are hydrothermal-dominated type, and unlike the total flow turbine +t of the present invention and conventional steam turbine systems, the sensible heat of hot water can also be used, and the steam turbine σ ) function, the latent heat of steam can also be used, so it is more efficient than the steam turbine method or other two-phase flow turbine-only methods without having to lower the two-phase flow nozzle outlet pressure too much. Good luck to the reinjection well σ] There is no need to lower the humidity and temperature, and scale adhesion can be prevented.
なお、本発明のトータルフロータ−ビン装置は地熱発電
の分野しこおいて有効（こ適用することができる。Incidentally, the total flow turbine device of the present invention can be effectively applied to the field of geothermal power generation.
第１図は従来の二相流タービンと蒸気タービンを組合せ
て使用した発電装置の系統図、第２図は本発明の実施例
１におけるトークルフロータービン装置の概略側断面図
であり、第３図番ま第２図の系統図、第４図は本発明の
実施例２におけるトータルフロータ−ビン装置の概略側
断面図である。
１・・・二相流タービン、５・・・トータルフロータ−
ビン、６・・・二相流ノズル、９・・・ロータ、１０・
・・回転分離ドラム、１１・・・ディフューザ、１２・
・・蒸気タービン、１２Ａ・・・ノズル、１２Ｂ・・・
回転羽根、１４・・・水車、ＷＳ・・・二相流、Ｓ・・
・蒸気、Ｗ・・・熱水。
代理人 弁理士 小 川 信 −
弁理士 野 口 賢 照
弁理士 斎 下 和 彦FIG. 1 is a system diagram of a power generation device using a conventional two-phase flow turbine and a steam turbine in combination, FIG. 2 is a schematic side sectional view of a torque flow turbine device in Embodiment 1 of the present invention, and FIG. 2 is a system diagram, and FIG. 4 is a schematic side sectional view of a total flow turbine device according to a second embodiment of the present invention. 1... Two-phase flow turbine, 5... Total floater
Bottle, 6... Two-phase flow nozzle, 9... Rotor, 10.
... Rotating separation drum, 11... Diffuser, 12.
...Steam turbine, 12A...Nozzle, 12B...
Rotating blade, 14...water wheel, WS...two-phase flow, S...
・Steam, W...Hot water. Agent: Patent Attorney Makoto Ogawa − Patent Attorney: Ken Noguchi Patent Attorney: Kazuhiko Saishita
Claims (1)
相流を形成し、その高速二相流をローータＧこ設けた回
転分離ドラムにて蒸気と熱水とＧこ分離させる二相流タ
ービンにおいて、分離さレタ蒸気の熱エネルギーを該回
転分離ドラムの外周に設けられた蒸気タービンにより動
力に変換可能とすると共に、分離、された熱水の熱エネ
ルギーをその熱水が該回転分離ドラムがらディフューザ
部経由排出される際に動力に変換可能としたことを特徴
としたトータルフロータ−ビン装置。Hot water or two-phase flow is expanded from a two-phase flow nozzle to form a high-speed two-phase flow, and the high-speed two-phase flow is separated into steam and hot water in a rotating separation drum equipped with a rotor. In the flow turbine, the thermal energy of the separated steam can be converted into power by a steam turbine installed on the outer periphery of the rotary separation drum, and the thermal energy of the separated hot water can be converted into power by the rotary separation drum. A total flow turbine device characterized by being able to convert drum debris into power when it is discharged through a diffuser section.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23021982A JPS59122702A (en) | 1982-12-29 | 1982-12-29 | Total flow turbine device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23021982A JPS59122702A (en) | 1982-12-29 | 1982-12-29 | Total flow turbine device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS59122702A true JPS59122702A (en) | 1984-07-16 |
| JPH0115681B2 JPH0115681B2 (en) | 1989-03-20 |
Family
ID=16904419
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP23021982A Granted JPS59122702A (en) | 1982-12-29 | 1982-12-29 | Total flow turbine device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59122702A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5385446A (en) * | 1992-05-05 | 1995-01-31 | Hays; Lance G. | Hybrid two-phase turbine |
| US5664420A (en) * | 1992-05-05 | 1997-09-09 | Biphase Energy Company | Multistage two-phase turbine |
| US5685691A (en) * | 1996-07-01 | 1997-11-11 | Biphase Energy Company | Movable inlet gas barrier for a free surface liquid scoop |
| US5750040A (en) * | 1996-05-30 | 1998-05-12 | Biphase Energy Company | Three-phase rotary separator |
| US6090299A (en) * | 1996-05-30 | 2000-07-18 | Biphase Energy Company | Three-phase rotary separator |
-
1982
- 1982-12-29 JP JP23021982A patent/JPS59122702A/en active Granted
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5385446A (en) * | 1992-05-05 | 1995-01-31 | Hays; Lance G. | Hybrid two-phase turbine |
| WO1996023129A1 (en) * | 1992-05-05 | 1996-08-01 | Biphase Energy Company | Hybrid two-phase turbine |
| US5664420A (en) * | 1992-05-05 | 1997-09-09 | Biphase Energy Company | Multistage two-phase turbine |
| US5720799A (en) * | 1992-05-05 | 1998-02-24 | Biphase Energy Company | Multistage two-phase turbine |
| US5946915A (en) * | 1992-05-05 | 1999-09-07 | Biphase Energy Company | Multistage two-phase turbine |
| US6122915A (en) * | 1992-05-05 | 2000-09-26 | Biphase Energy Company | Multistage two-phase turbine |
| US6314738B1 (en) | 1992-05-05 | 2001-11-13 | Biphase Energy Company | Multistage two-phase turbine |
| US5750040A (en) * | 1996-05-30 | 1998-05-12 | Biphase Energy Company | Three-phase rotary separator |
| US6090299A (en) * | 1996-05-30 | 2000-07-18 | Biphase Energy Company | Three-phase rotary separator |
| US5685691A (en) * | 1996-07-01 | 1997-11-11 | Biphase Energy Company | Movable inlet gas barrier for a free surface liquid scoop |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0115681B2 (en) | 1989-03-20 |
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