JPS6346360B2 - - Google Patents
Info
- Publication number
- JPS6346360B2 JPS6346360B2 JP58044414A JP4441483A JPS6346360B2 JP S6346360 B2 JPS6346360 B2 JP S6346360B2 JP 58044414 A JP58044414 A JP 58044414A JP 4441483 A JP4441483 A JP 4441483A JP S6346360 B2 JPS6346360 B2 JP S6346360B2
- Authority
- JP
- Japan
- Prior art keywords
- tube
- fluid
- heat exchanger
- shell
- heat transfer
- 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
- 239000012530 fluid Substances 0.000 claims description 84
- 238000005452 bending Methods 0.000 claims 1
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details Of Heat-Exchange And Heat-Transfer (AREA)
Description
【発明の詳細な説明】
〔発明の利用分野〕
本発明は多管式熱交換器に係り、特に高温ガス
炉用蒸気発生器に使用する好適な胴側流体入口形
状を備えた多管式熱交換器に関する。[Detailed Description of the Invention] [Field of Application of the Invention] The present invention relates to a shell-and-tube heat exchanger, and particularly to a shell-and-tube heat exchanger with a shell-side fluid inlet shape suitable for use in a steam generator for a high-temperature gas furnace. Regarding the exchanger.
従来の多管式熱交換器を第１図及び第２図によ
り説明する。
A conventional shell-and-tube heat exchanger will be explained with reference to FIGS. 1 and 2.
多数の伝熱管４は管板６に取り付けられ、胴３
内に収容されている。管内流体は流入口７からベ
ダ１０を経へ、各伝熱管４内を通り、ベダ１０、
流出口９へと流れる。胴側流体は入口ノズル１か
ら伝熱管４の管群に流入し、多数の邪魔板５によ
つて管群内とジグザク状に屈曲流動し出口ノズル
８から放出される。 A large number of heat exchanger tubes 4 are attached to a tube sheet 6, and the shell 3
is housed within. The fluid in the tube passes from the inlet 7 to the beda 10, passes through each heat transfer tube 4, and passes through the beda 10,
It flows to the outlet 9. The shell-side fluid flows into the tube group of heat transfer tubes 4 from the inlet nozzle 1, flows in a zigzag manner within the tube group by a large number of baffle plates 5, and is discharged from the outlet nozzle 8.
このような多管式熱交換器では、胴側流体の流
量が多い場合には、伝熱管の摩耗や振動振止のた
めに、胴側流体入口部に緩衝板２が取り付けられ
た。すなわち第２図に示すように従来の多管式熱
交換器の流入部バツフル１段目では、胴側流体が
入口ノズル１を通り、胴３内に流入する際、直接
伝熱管４に当らぬよう緩衝板２が設けられてい
る。このような流入構造の場合、緩衝板２に当つ
た胴側流体は、胴３の内壁に沿つて矢印１１の方
向に備流する。管群外周部の胴側流体の流れは速
いが、緩衝板２の後方の管群内部の流れはよどむ
か非常に遅くなる。このため各伝熱管４の伝熱性
能を均一にすることができず、各伝熱管４の伝熱
特性がアンバランスとなる欠点があつた。 In such a shell-and-tube heat exchanger, when the flow rate of the shell-side fluid is large, a buffer plate 2 is attached to the shell-side fluid inlet to prevent wear and vibration of the heat transfer tubes. In other words, as shown in FIG. 2, in the first stage of the inflow section of the conventional multi-tube heat exchanger, when the shell-side fluid passes through the inlet nozzle 1 and flows into the shell 3, it does not directly hit the heat transfer tubes 4. A buffer plate 2 is provided. In the case of such an inflow structure, the body-side fluid that hits the buffer plate 2 flows along the inner wall of the body 3 in the direction of the arrow 11. Although the flow of the body-side fluid at the outer periphery of the tube group is fast, the flow inside the tube group behind the buffer plate 2 stagnates or becomes very slow. For this reason, the heat transfer performance of each heat exchanger tube 4 could not be made uniform, and there was a drawback that the heat transfer characteristics of each heat exchanger tube 4 became unbalanced.
本発明の目的は、伝熱管の耐摩耗性と振動防止
性に優れ、かつ伝熱管各部の伝熱特性のバランス
を均一にする多管式熱交換器を提供することであ
る。
An object of the present invention is to provide a multi-tube heat exchanger that has excellent wear resistance and anti-vibration properties of heat exchanger tubes, and has a uniform balance of heat transfer characteristics in each part of the heat exchanger tubes.
本発明は、多管式熱交換器の胴側流体入口部に
おいて、前記入口部の伝熱管群の一部分を包囲す
ると共に胴側流体入口部に通じる開口端を有する
流体案内筒を設け、胴側流体を伝熱管群の管軸方
向にジグザグ状に屈曲流動させる邪魔板の切欠き
部を前記流体案内筒の内側に、かつ胴側流体流入
側に設けたことが特徴である。このため、胴側流
体入口部に流入するノズル流は一度流体案内筒と
胴側の間隙を流れるので、ノズル流による伝熱管
への衝撃が緩和され、そして、前記間隙内の流れ
は徐々に流体案内筒の開口端を乗り越えながら管
群内に流入し、ノズル流と反対方向に管群内を流
れるので、管群内の流れは一様となり、各伝熱管
の伝熱特性が均一になる。
The present invention provides a fluid guide cylinder that surrounds a part of the heat transfer tube group in the inlet section and has an open end communicating with the shell side fluid inlet section in the shell side fluid inlet section of a shell-and-tube heat exchanger. A feature is that a notch in the baffle plate that causes the fluid to flow in a zigzag manner in the tube axis direction of the heat transfer tube group is provided inside the fluid guide cylinder and on the fluid inflow side of the body side. Therefore, the nozzle flow that flows into the body-side fluid inlet section once flows through the gap between the fluid guide tube and the body side, so the impact on the heat transfer tube due to the nozzle flow is alleviated, and the flow in the gap gradually changes. It flows into the tube group while overcoming the open end of the guide tube and flows in the tube group in the opposite direction to the nozzle flow, so that the flow within the tube group becomes uniform and the heat transfer characteristics of each heat transfer tube become uniform.
以下、本発明の一実施例を第３図、第４図によ
り説明する。第３図は、本発明での流体案内筒付
きの多管式熱交換器で、第４図は第３図のＢ―Ｂ
断面である。なお、第１図と同一物或いは同等物
は、第１図と同一番号をつけた。
An embodiment of the present invention will be described below with reference to FIGS. 3 and 4. Fig. 3 shows a multi-tubular heat exchanger with a fluid guide cylinder according to the present invention, and Fig. 4 shows B-B in Fig. 3.
It is a cross section. Components that are the same as or equivalent to those in FIG. 1 are given the same numbers as in FIG. 1.
上部および下部ヘツダ１０に接した上下の管板
６に挾まれた多数の伝熱管群４の間に適宜間隔に
欠切き形の邪魔板５，５′が切欠き部の位置が交
互になるように配置されている。本発明において
は、第１邪魔板５による第１の切欠き部は胴側流
体入口１側に配置されている。そして伝熱管群４
の管軸方向を一部分包むように円筒形の流体案内
筒２′が第１邪魔板５に取り付けられてある。第
１邪魔板５は第５図に示すような形状をしてお
り、円形の邪魔板を欠円状にくり抜いたものであ
る。流体案内筒２′の内半径は、この欠円部の半
径より大きく、第１邪魔板に接している。流体案
内筒２′の高さは第１邪魔板から計つて胴側流体
入口部１よりも高くなるようにとつてある。第２
以降の邪魔板５′は第５図に示すように従来型の
切欠き型の邪魔板である。 Notch-shaped baffle plates 5, 5' are provided at appropriate intervals between a large number of heat transfer tube groups 4 sandwiched between upper and lower tube plates 6 in contact with the upper and lower headers 10, and the positions of the notches are alternated. It is arranged like this. In the present invention, the first notch formed by the first baffle plate 5 is arranged on the body side fluid inlet 1 side. And heat exchanger tube group 4
A cylindrical fluid guide tube 2' is attached to the first baffle plate 5 so as to partially enclose the tube axis direction. The first baffle plate 5 has a shape as shown in FIG. 5, and is formed by hollowing out a circular baffle plate in the form of a missing circle. The inner radius of the fluid guide tube 2' is larger than the radius of this missing circular portion, and is in contact with the first baffle plate. The height of the fluid guide tube 2' is set to be higher than the body side fluid inlet section 1 as measured from the first baffle plate. Second
The subsequent baffle plate 5' is a conventional notch type baffle plate as shown in FIG.
この場合に、管内側流体は管内側流体入口ノズ
ル７より下部ヘツダ１０に入り、並列して置かれ
た多数の伝熱管４内を流れ、上部ヘツダに集まり
管内側流体入口ノズル９を通つて流出する。胴側
流体は胴側流体入口ノズル１より入り、円筒状の
流体案内筒２′にぶつかり胴３の外周部に沿つて
流れる。そして、徐々に管板６と流体案内筒２′
の間を流体案内筒２′を乗りこえるようにして流
れ、伝熱管４の管群内に流入する。さらに、胴側
流体は入口ノズル１の流れと反対方向に伝熱管群
４の間を通り、第１邪魔板５による切欠き部１２
を通つて第１邪魔板５と第２邪魔板５′により構
成される折流部へ流入する。その後、胴側流体は
伝熱管群４の間を邪魔板５により流れが次々に曲
げられるために蛇行して流れ、胴側流体出口ノズ
ル８より外部へ流出する。 In this case, the tube inner fluid enters the lower header 10 from the tube inner fluid inlet nozzle 7, flows through a large number of heat transfer tubes 4 placed in parallel, collects in the upper header, and flows out through the tube inner fluid inlet nozzle 9. do. The body-side fluid enters through the body-side fluid inlet nozzle 1, collides with the cylindrical fluid guide cylinder 2', and flows along the outer circumference of the body 3. Then, gradually the tube plate 6 and the fluid guide tube 2'
The fluid flows through the fluid guide cylinder 2' and flows into the tube group of the heat transfer tubes 4. Further, the body side fluid passes between the heat transfer tube group 4 in the opposite direction to the flow of the inlet nozzle 1, and passes through the notch 12 formed by the first baffle plate 5.
The water flows through the flow into the folded part formed by the first baffle plate 5 and the second baffle plate 5'. After that, the shell-side fluid flows in a meandering manner between the heat transfer tube group 4 because the flow is successively bent by the baffle plate 5, and flows out from the shell-side fluid outlet nozzle 8 to the outside.
この場合、管板６と第１邪魔板５により構成さ
れる第１の折流区間において、胴側流体入口部１
より流入した胴側流体は、管板６と流体案内胴
２′の間の隙間の全ての円周上の位置から管群４
内に流入するようになる。このため、従来緩衝板
２の後方に生じていた渦流の掟み域がなくなり、
各位置における伝熱管の伝熱特性のバランスが改
善される。また、流体案内筒２′がある事により、
胴側流体入口より入つてくる胴側流体が伝熱管４
に直接当ることがないために、伝熱管４の摩耗お
よび振動に対する信頼性が向上する。 In this case, in the first folded flow section constituted by the tube plate 6 and the first baffle plate 5, the body side fluid inlet section 1
The body-side fluid that has flowed in from all positions on the circumference of the gap between the tube plate 6 and the fluid guide body 2' flows through the tube group 4.
It begins to flow inside. For this reason, the distorted area of the vortex that conventionally occurred behind the buffer plate 2 is eliminated.
The balance of heat transfer characteristics of the heat transfer tubes at each position is improved. In addition, due to the presence of the fluid guide cylinder 2',
The shell-side fluid entering from the shell-side fluid inlet flows into the heat transfer tube 4.
Since the heat exchanger tubes 4 do not come into direct contact with the heat exchanger tubes 4, reliability against wear and vibration is improved.
第７図は、本発明の他の実施例である。本実施
例においては、熱交換器の胴３の胴側流体入口部
１の付近がふくらんでおり、流体案内筒２′はこ
のふくらみの境界の部分についている。邪魔板
５，５′は全て第６図に示すような従来型の欠円
形のものである。流体案内筒２′は、前記第１の
実施例と同じく円筒状をしており、高さも第１邪
魔板５から測つて胴側流体入口部１よりも高くな
るようにとつてある。本実施例によれば、胴３の
外周に沿つた胴側流体が流体案内筒２′を乗り越
えて管群４に入るときに、前記第１の実施例に比
べてゆつくり入るようになるため、伝熱管４の伝
熱特性のバランスがさらに向上するという効果が
ある。 FIG. 7 shows another embodiment of the invention. In this embodiment, the body 3 of the heat exchanger has a bulge near the body-side fluid inlet 1, and the fluid guide cylinder 2' is located at the boundary of this bulge. The baffle plates 5, 5' are all of the conventional type with a notched circular shape as shown in FIG. The fluid guide tube 2' has a cylindrical shape as in the first embodiment, and its height is set higher than the body side fluid inlet section 1 as measured from the first baffle plate 5. According to this embodiment, when the shell-side fluid along the outer circumference of the shell 3 passes over the fluid guide tube 2' and enters the tube group 4, it enters more slowly than in the first embodiment. This has the effect of further improving the balance of heat transfer characteristics of the heat transfer tubes 4.
第８図は、本発明の第３の実施例であり、本実
施例においては流体案内筒２′の高さを胴側流体
入口部１側で一番高く、反対側で一番低くなるよ
うにしたものである。流体案内筒２′の高さは、
胴側流体入口部１側で、入口部１よりも高くなる
ようにとつてあり、高さの勾配は直線的に変化し
ている。本実施例によれば、胴側流体入口部１よ
り入つた胴側流体が流体案内筒２′を乗り越えて
伝熱管群４に流入する際の圧損が減少するという
利点がある。 FIG. 8 shows a third embodiment of the present invention. In this embodiment, the height of the fluid guide cylinder 2' is set to be highest on the body side fluid inlet 1 side and lowest on the opposite side. This is what I did. The height of the fluid guide cylinder 2' is
The body-side fluid inlet section 1 side is set higher than the inlet section 1, and the gradient of the height changes linearly. According to this embodiment, there is an advantage that the pressure loss when the shell-side fluid entering from the shell-side fluid inlet portion 1 passes over the fluid guide tube 2' and flows into the heat exchanger tube group 4 is reduced.
本実施例においては流体案内筒の高さを直線勾
配で変化するとしたが、必ずしも直線勾配で変化
する必要はない。 In this embodiment, the height of the fluid guide tube is changed with a linear gradient, but it does not necessarily need to be changed with a linear gradient.
第９図は、本発明の第４の実施例であり、本実
施例においては、流体案内筒の形状が長円形にな
つており、流体案内筒２′は、胴３との距離が胴
側流体入口部１側で広く、反対側の端部で狭くな
るように設置されている。バツフル５の形状は、
円形の邪魔板を欠円状にくり抜いたものであり、
バツフル５と流体案内筒２′は密接している。本
実施例によれば、胴側流体入口部１より流入した
胴側流体は、胴３と流体案内筒２′の間を流れる
際に端部に向うにつれ抵抗が増すようになるため
に、流体案内筒２′の全周上から管群４に流入し
やすくなるという利点がある。 FIG. 9 shows a fourth embodiment of the present invention. In this embodiment, the shape of the fluid guide tube is oval, and the distance between the fluid guide tube 2' and the body 3 is on the body side. It is installed so that it is wide at the fluid inlet section 1 side and narrow at the opposite end. The shape of Batsuful 5 is
It is a circular baffle board cut out into an occluded shape,
The baffle 5 and the fluid guide tube 2' are in close contact. According to this embodiment, when the body-side fluid flowing in from the body-side fluid inlet 1 flows between the body 3 and the fluid guide tube 2', the resistance increases as it goes toward the end. There is an advantage that it becomes easier to flow into the tube group 4 from above the entire circumference of the guide tube 2'.
本実施例においては、胴側流体入口部１の反対
側端部において胴３と流体案内筒２′との間に隙
間が残つているが、必ずしも隙間が残つている必
要はない。また、流体案内筒２′の形状も必ずし
も長円形である必要はなく、流体案内筒２′は胴
３に対して偏心して設置できるような形状であれ
ば何でも良い。 In this embodiment, a gap remains between the body 3 and the fluid guide cylinder 2' at the opposite end of the body-side fluid inlet 1, but it is not necessary that the gap remains. Further, the shape of the fluid guide tube 2' does not necessarily have to be oval, and any shape may be used as long as the fluid guide tube 2' can be installed eccentrically with respect to the body 3.
また、以上の各実施例においては流体案内筒
２′の形状を円筒状としたが、必ずしも円筒状で
ある必要はなく、多角形などであつても良い。 Further, in each of the above embodiments, the fluid guide cylinder 2' has a cylindrical shape, but it does not necessarily have to be cylindrical, and may be polygonal or the like.
以上のように、本発明によれば、胴側流体入口
部に流入した流体は流体案内筒の外周に沿いなが
ら、その開口端を乗り越えて伝熱管群内に一様に
流れるので、多管式熱交換器入口部における伝熱
管各部の伝熱特性のバランスを均一にし、かつ伝
熱管の耐摩耗性および振動防止性を向上させるこ
とができる。このため、熱交換器の信頼性を著し
く高めることができ、工事上大いに貢献する。
As described above, according to the present invention, the fluid flowing into the body-side fluid inlet portion flows uniformly into the heat transfer tube group by overcoming the open end while following the outer periphery of the fluid guide tube. It is possible to uniformly balance the heat transfer characteristics of each part of the heat exchanger tube at the inlet of the heat exchanger, and to improve the wear resistance and vibration prevention properties of the heat exchanger tube. Therefore, the reliability of the heat exchanger can be significantly improved, which greatly contributes to construction work.
第１図は従来型の緩衝板付きの多管式熱交換器
であり、第２図は第１図のＡ―Ａ断面図である。
第３図は本発明の一実施例になる多管式熱交換器
の縦断面図、第４図は第３図のＢ―Ｂ断面図であ
る。第５図、第６図は各々本発明での邪魔板の形
状図であり、第７図は本発明の第二の実施例を示
す縦断面図、第８図は本発明の第三の実施例を示
す縦断面図、第９図は、本発明の第四の実施例を
示す縦断面図である。
１…胴側流体入口部、２…緩衝板、２′…包囲
板、３…胴、４…伝熱管、５…（欠円形）邪魔
板、６…管板、７…管内側流体入口ノズル、８…
胴側流体出口ノズル、９…管内流体出口ノズル、
１０…ヘツダ、１２…邪魔板の切欠き部、１１…
矢印。
FIG. 1 shows a conventional shell-and-tube heat exchanger with a buffer plate, and FIG. 2 is a sectional view taken along line AA in FIG.
FIG. 3 is a longitudinal sectional view of a shell-and-tube heat exchanger according to an embodiment of the present invention, and FIG. 4 is a sectional view taken along line BB in FIG. 5 and 6 are diagrams showing the shape of the baffle plate according to the present invention, FIG. 7 is a vertical sectional view showing a second embodiment of the present invention, and FIG. 8 is a diagram showing a third embodiment of the present invention. FIG. 9 is a vertical cross-sectional view showing a fourth embodiment of the present invention. DESCRIPTION OF SYMBOLS 1...Body side fluid inlet part, 2...Buffer plate, 2'...Surrounding plate, 3...Body, 4...Heat transfer tube, 5...(missed circular) baffle plate, 6...Tube plate, 7...Tube inside fluid inlet nozzle, 8...
Body side fluid outlet nozzle, 9... pipe fluid outlet nozzle,
10... Header, 12... Notch part of baffle plate, 11...
arrow.
Claims (1)
多数の邪魔板によつて折流区間に分割し、胴側流
体を伝熱管群の管軸方向に対してジグザグ状に屈
曲流動させる多管式熱交換器において、胴側流体
が前記伝熱管群に最初に流入する第１折流区間の
胴側流体入口部に、この区間の発熱管管群を一部
分包囲すると共に胴側流体入口部に通じる開口端
を有する円筒形または多角形の流体案内筒を設
け、第一折流区間から次の折流区間に胴側流体を
導びく第一邪魔板の切欠き部を流体案内筒の内側
にかつ胴側流体流入側に設けたことを特徴とする
多管式熱交換器。 ２ 前記第１項において、前記流体案内筒の高さ
を、胴側流体入口側より端部に向つて変化させた
ことを特徴とする多管式熱交換器。 ３ 前記第１項において、前記流体案内筒の位置
を、胴の中心に対して偏心させて設けた事を特徴
とする多管式熱交換器。[Claims] 1. The tube axis direction of the heat transfer tube group installed between the tube sheets is divided into folded flow sections by a large number of baffles, and the body side fluid is directed in the tube axis direction of the heat transfer tube group. In a multi-tubular heat exchanger that causes bending flow in a zigzag pattern, the body side fluid inlet part of the first folded flow section where the body side fluid first flows into the heat transfer tube group partially surrounds the heat generating tube group in this section. At the same time, a cylindrical or polygonal fluid guide tube having an open end communicating with the body-side fluid inlet section is provided, and a cutout in the first baffle plate guides the body-side fluid from the first folded flow section to the next folded flow section. A multi-tubular heat exchanger characterized in that a part is provided inside a fluid guide tube and on a fluid inflow side of a shell side. 2. The multi-tubular heat exchanger according to item 1, characterized in that the height of the fluid guide cylinder is changed from the body side fluid inlet side toward the end. 3. The shell-and-tube heat exchanger according to item 1 above, wherein the fluid guide tube is located eccentrically with respect to the center of the shell.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4441483A JPS59170697A (en) | 1983-03-18 | 1983-03-18 | Heat exchange of multi-pipe type |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP4441483A JPS59170697A (en) | 1983-03-18 | 1983-03-18 | Heat exchange of multi-pipe type |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS59170697A JPS59170697A (en) | 1984-09-26 |
| JPS6346360B2 true JPS6346360B2 (en) | 1988-09-14 |
Family
ID=12690838
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP4441483A Granted JPS59170697A (en) | 1983-03-18 | 1983-03-18 | Heat exchange of multi-pipe type |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59170697A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH07502357A (en) * | 1991-12-27 | 1995-03-09 | アール・アンド・ディー・アソシエイツ | Fast converging projective neural network |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5425415A (en) * | 1993-06-15 | 1995-06-20 | Abb Lummus Crest Inc. | Vertical heat exchanger |
| CN103486561A (en) * | 2013-09-22 | 2014-01-01 | 桂林新艺制冷设备有限责任公司 | Compact smoke waste heat recovery and steam generating device |
| KR102444996B1 (en) * | 2016-07-19 | 2022-09-20 | 러머스 테크놀러지 인코포레이티드 | Feed Outflow Heat Exchanger |
| CN208332761U (en) | 2018-01-16 | 2019-01-04 | 开利公司 | Deflector for condenser, the condenser with it and refrigeration system |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6242241Y2 (en) * | 1981-05-11 | 1987-10-29 |
-
1983
- 1983-03-18 JP JP4441483A patent/JPS59170697A/en active Granted
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH07502357A (en) * | 1991-12-27 | 1995-03-09 | アール・アンド・ディー・アソシエイツ | Fast converging projective neural network |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS59170697A (en) | 1984-09-26 |
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