JPS6149997A - Heat transfer tube supporting mechanism - Google Patents
Heat transfer tube supporting mechanismInfo
- Publication number
- JPS6149997A JPS6149997A JP16998084A JP16998084A JPS6149997A JP S6149997 A JPS6149997 A JP S6149997A JP 16998084 A JP16998084 A JP 16998084A JP 16998084 A JP16998084 A JP 16998084A JP S6149997 A JPS6149997 A JP S6149997A
- Authority
- JP
- Japan
- Prior art keywords
- sleeve
- heat transfer
- transfer tube
- heat exchanger
- exchanger tube
- 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.)
- Pending
Links
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
- F28F9/007—Auxiliary supports for elements
- F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は蒸気発生器や熱交換器で用いられる伝熱管を安
定に支持することのできる伝熱管支持機溝に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a heat exchanger tube support groove capable of stably supporting heat exchanger tubes used in steam generators and heat exchangers.
〔従来の技１イ、ｉ〕
ヘリウムガスタービン発電、ランキンサイクル発電、そ
の他の中間だ）交換器等にあっては、伝熱管を用いた熱
エネルギの輸送が行われている。この伝熱管内に充填さ
れて熱エネルギの輸送に携わる二次熱媒体としては、蒸
気、水素ガス、ヘリウムガス等がその用途に応じて用い
られる。[Conventional Techniques 1, I] Helium gas turbine power generation, Rankine cycle power generation, and other intermediate systems) In exchangers, etc., thermal energy is transported using heat transfer tubes. Steam, hydrogen gas, helium gas, etc. are used as the secondary heat medium filled in the heat transfer tube and involved in transporting thermal energy, depending on the purpose.
ところで伝熱管による熱輸送効率を高めるには、−次熱
媒体中に設けられる伝熱管の長さを十分に長くすること
が必要となる。またその熱伝達率を高めるには、上記伝
熱管の周囲を流れる一次熱媒体の流速を高める必要があ
る。この為、伝熱管を狭い間隙を形成して螺旋状に巻回
する等して、所謂ヘリカルコイル状にして用いられるこ
とが多い。By the way, in order to increase the heat transport efficiency by the heat exchanger tube, it is necessary to make the length of the heat exchanger tube provided in the -order heat medium sufficiently long. Further, in order to increase the heat transfer coefficient, it is necessary to increase the flow velocity of the primary heat medium flowing around the heat exchanger tube. For this reason, heat transfer tubes are often used in the form of a so-called helical coil, such as by spirally winding the tubes with a narrow gap formed therebetween.
これ故、伝熱管間の相互接触を防止し、且つ上記伝熱管
間の間隔を一定に保って均一な冷却を行いつつ、そのホ
ットスポットを防止し、更に伝熱管の白瓜を支えて、−
次熱媒体の流れによる振動を抑える上で、前記伝熱管を
数箇所において支持固定することが必要である。そこで
従来では、例えば第５図に示すように、伝熱管１をスリ
ーブ２を介して支持板３に支持固定するようにしている
。Therefore, it prevents the heat exchanger tubes from coming into contact with each other, and maintains a constant spacing between the heat exchanger tubes for uniform cooling, prevents hot spots, and supports the white melons of the heat exchanger tubes.
In order to suppress vibrations caused by the flow of the heat medium, it is necessary to support and fix the heat transfer tube at several locations. Therefore, conventionally, as shown in FIG. 5, for example, the heat exchanger tube 1 is supported and fixed to a support plate 3 via a sleeve 2.
ところが前述したように伝熱管１はヘリ力ルコイル形状
を有し、成る曲率を有している。この為、上記形状の伝
熱管１を安定に、且つ確実に支持するべくスリーブ２の
高い加工債度と、組立て１青度が要求された。また、高
１ガス炉用の蒸気発生器や中間熱交換器等にあっては、
−次熱媒体中における伝熱管は１０００°Ｃ程度に加熱
される。この為、伝熱管１が熱膨張による伸びを生じ、
その支持部において前記スリーブ２との間ですべりを発
生する。また伝熱管１を横切って高速に流れる一次熱媒
体のカルマン渦等の為に前記伝熱管１が流体振動を生じ
、この流体振動によって前記支持部にすべりやたっきが
発生する。However, as described above, the heat exchanger tube 1 has a helical coil shape and has a curvature. Therefore, in order to stably and reliably support the heat exchanger tube 1 having the above-mentioned shape, the sleeve 2 was required to have a high degree of machining accuracy and a high degree of assembly. In addition, for steam generators and intermediate heat exchangers for high-1 gas furnaces,
- The heat exchanger tube in the next heat medium is heated to about 1000°C. For this reason, the heat exchanger tube 1 stretches due to thermal expansion,
Slip occurs between the supporting portion and the sleeve 2. Further, due to the Karman vortex of the primary heat medium flowing at high speed across the heat exchanger tube 1, fluid vibration occurs in the heat exchanger tube 1, and this fluid vibration causes slipping and knocking in the support portion.
ところで上記伝熱管１は、一般に１０００℃程度の高温
に耐え１ｑるようにハステロイＡｂインコネル等の超合
金で溝成される。このような超合金材は、−次熱媒体で
あるヘリウムガス中で、その表面酸化被膜の形成修復が
行われないことから、上記支持部で金属凝着を生じる危
険性がある。そこで、従来より前記スリーブ２のすべり
面にＺｒＯ２やＣｒ２．Ｃ＋；等のセラミック溶射材を
コーティングして上述した不具合を回避するべく工夫が
施されている。By the way, the heat exchanger tube 1 is generally made of a superalloy such as Hastelloy Ab-Inconel so as to withstand high temperatures of about 1000°C. In such a superalloy material, the formation and repair of the surface oxide film is not performed in helium gas, which is a secondary heat medium, and therefore there is a risk of metal adhesion occurring on the support portion. Therefore, ZrO2, Cr2. Efforts have been made to avoid the above-mentioned problems by coating with a ceramic spraying material such as C+;.
然し乍ら一般に、上記スリーブ２の内径は、伝熱管１の
外径より幾分大きめに設定される為、両者間にカフが生
じ易く、次のような不具合を来たす。例えば伝熱管１と
スリーブ２との閂のミスアライメントによって上記スリ
ーブ２の端部で所謂片当りが生じ、その過大な面圧よっ
て異常摩耗を招来する。また上記伝熱管１とスリーブ２
との間のガタによって、繰返したつきに起因する前記セ
ラミック溶射部の疲労クランクが発生し易い。更には前
記伝熱管１が曲率を有する為、スリーブ２との全面接触
が困難となり、これに起因する上記片当りが生じて上述
した問題をＩＢ来し易い。However, since the inner diameter of the sleeve 2 is generally set to be somewhat larger than the outer diameter of the heat transfer tube 1, a cuff tends to form between the two, resulting in the following problems. For example, misalignment of the bolts between the heat exchanger tube 1 and the sleeve 2 causes so-called one-sided contact at the end of the sleeve 2, and the excessive surface pressure causes abnormal wear. In addition, the heat exchanger tube 1 and sleeve 2
Due to the backlash between the two parts, fatigue cranking of the ceramic sprayed part due to repeated contact is likely to occur. Furthermore, since the heat exchanger tube 1 has a curvature, it is difficult to make full-surface contact with the sleeve 2, which causes the uneven contact described above, which tends to cause the above-mentioned problem IB.
本発明はこのような事情を考慮してなされたもので、そ
の目的とするところは、上述した異常四耗や疲労クラッ
ク発生等の不具合を招くことなしに伝熱管を安定に支持
することのできる簡易な溝道の伝熱管支持機構を提供す
ることにある。The present invention has been made in consideration of these circumstances, and its purpose is to stably support heat exchanger tubes without causing problems such as the above-mentioned abnormal wear and fatigue cracks. The object of the present invention is to provide a simple groove-channel heat exchanger tube support mechanism.
本発明は伝熱管を囲繞して設けられるスリーブを、上記
伝熱管と同じ曲率を有し、且つ軸方向にスリットを設け
た溝道とし、外周に設けたテーパ螺子をグリッドにねじ
込んで縮径する袋ナツトを用いて前記伝熱管を囲繞した
スリーブの両端をそれぞれ締付けることによって、前記
スリーブを伝熱管に全面接触させ、このスリーブを介し
て前記伝熱管を上記グリッドに固定支持するようにした
ものである。In the present invention, a sleeve provided surrounding a heat exchanger tube has the same curvature as the heat exchanger tube and is a groove with a slit in the axial direction, and a tapered screw provided on the outer periphery is screwed into the grid to reduce the diameter. By tightening both ends of the sleeve surrounding the heat exchanger tube using cap nuts, the sleeve is brought into full contact with the heat exchanger tube, and the heat exchanger tube is fixedly supported on the grid via this sleeve. be.
かくして本発明によれば、スリットを有するスリーブが
袋ナツトの縮径によって伝熱管に全面接触して伝熱管を
支持するので、例えば伝熱管の周囲を流れる一次熱媒体
の温度変化によって該伝熱管が熱膨張または熱収縮して
も、伝熱管とスリーブとの間は全面接触状態を保って、
そのセラミックコーティング面で滑る。これ故、伝熱管
支持部の拘束力は摩１察力だけとなり、その値をかなり
小さく抑えることが可能となる。また伝熱管の周囲を流
れる一次熱媒体のカルマン描写によって伝熱管に流体振
動が発生するが、伝熱管支持部はスリーブを介してプリ
ロードを掛けた状態でグリッドに取付けられている為、
上記流体振動に起因する加振力に対して固定端として作
用する。これ故、所謂ガタ等によるたつきが発生せず、
伝熱管の振動振幅を小さく抑えることが可能となる。Thus, according to the present invention, the sleeve having the slit fully contacts the heat exchanger tube and supports the heat exchanger tube by reducing the diameter of the cap nut. Even when thermally expanded or contracted, the heat exchanger tube and sleeve maintain full contact,
It slides on its ceramic coated surface. Therefore, the restraining force of the heat exchanger tube support portion is only the frictional force, and it is possible to suppress the value to a considerably small value. In addition, fluid vibrations occur in the heat transfer tube due to the Karman description of the primary heat medium flowing around the heat transfer tube, but since the heat transfer tube support is attached to the grid with a preload applied through the sleeve,
It acts as a fixed end against the excitation force caused by the fluid vibration. Therefore, there is no wobbling due to so-called rattling,
It becomes possible to suppress the vibration amplitude of the heat exchanger tube to a small level.
従って伝熱管とスリーブ間の支持接触部の片当りがない
ので、過大な接触応力に起因するスチツクや異常摩耗が
未然に防がれる。故に、伝熱管の破壊を１３来するよう
な負荷が加わることがなく、伝熱管の信頼ｉ生の向上を
図り得る。また伝熱管とスリーブとの間の支持接触部の
ガタがない為、流体振動に起因するたつき摩耗を防止し
て、その耐摩耗性の向上を図り１ｎる。更には、スリー
ブの高い加工精度やその組立て精度を必要とせず、また
簡易な構造である為、そのコスト低減を図り（ｉる等の
実用上絶大なる効果が奏せられる。Therefore, since there is no uneven contact between the support contact portion between the heat transfer tube and the sleeve, stickiness and abnormal wear caused by excessive contact stress can be prevented. Therefore, the reliability of the heat exchanger tubes can be improved without applying a load that would cause the heat exchanger tubes to break. Furthermore, since there is no backlash in the supporting contact portion between the heat transfer tube and the sleeve, sagging wear caused by fluid vibration is prevented, and the wear resistance is improved. Furthermore, since the sleeve does not require high machining accuracy or assembly accuracy, and has a simple structure, it can achieve great practical effects such as cost reduction.
以下、図面を参照して本発明の一実施例につき説明する
。Hereinafter, one embodiment of the present invention will be described with reference to the drawings.
第１図は実施例に係る伝熱管の支持１段（：４の要部溝
底図で、第２図はそのＩ−Ｉ方向から見た（苫成図、第
３図は］−１１方向から見た閘成図である。Fig. 1 is a groove bottom view of the main part of the first stage of heat transfer tube support (:4) according to the embodiment, Fig. 2 is a view of the groove viewed from the I-I direction (completion view, Fig. 3 is the -11 direction) This is a diagram of the lock formation seen from.
図中１１はヘリカルコイル状に形成された伝熱管、１２
はスリーブ、１３はその外周にテーパ螺子を形成した袋
ナツト、また１４は上記袋ナラ１へ１３が螺合され、前
記スリーブ１２を介して前記伝熱管１１を支持するグリ
ッドである。In the figure, 11 is a heat exchanger tube formed in a helical coil shape, 12
1 is a sleeve, 13 is a cap nut having a tapered screw formed on its outer periphery, and 14 is a grid that 13 is screwed into the cap nut 1 and supports the heat exchanger tube 11 via the sleeve 12.
しかしてスリーブ１２は前記伝熱管１１の外径より僅か
に大きめの内径を有し、且つ伝熱管１１と同じ曲率を持
った筒体からなり、その周面に軸方向にスリット（切り
割）１２ａを形成している。このスリーブ１２は前記伝
熱管１１のヘリカル端部から伝熱管１１の所定の支持位
置に装管される。またスリーブ１２の内周面にはグルー
プＨｊ４＞’１２ｂが設けられており、前記スリット１
２ａを利用したスリーブ１２の縮径時に該スリーブ１２
の内周面に溶射コーティングされたセラミック溶射層１
２ｃが変形剥離しないようになっている。尚、上記セラ
ミック溶射層１２ｃは第４図に示すようにスリーブ１２
の内周面の上記グリープ１２ｂの形成部を除いて設けら
れるようになっている。またここでは上記グリープ１２
ｂは、前記スリット１２ａとの間で １２０°の角度を
為すように設けられているが、一般的には任意の角度で
複数本平行に設ければ良い。The sleeve 12 has an inner diameter slightly larger than the outer diameter of the heat exchanger tube 11, and is made of a cylinder having the same curvature as the heat exchanger tube 11, and has a slit (cut) 12a in the axial direction on its circumferential surface. is formed. This sleeve 12 is inserted into a predetermined support position of the heat exchanger tube 11 from the helical end of the heat exchanger tube 11 . Further, a group Hj4>'12b is provided on the inner peripheral surface of the sleeve 12, and the slit 1
When the diameter of the sleeve 12 is reduced using 2a, the sleeve 12
Ceramic sprayed layer 1 coated on the inner peripheral surface of
2c is designed to prevent deformation and peeling. The ceramic sprayed layer 12c is attached to the sleeve 12 as shown in FIG.
The grip 12b is formed on the inner peripheral surface of the grip 12b. Also here, the above Greep 12
b are provided so as to form an angle of 120° with the slit 12a, but generally a plurality of slits may be provided in parallel at any angle.
一方、前記袋ナツト１３は前記伝熱管１１の外径よりも
大きな内径を有し、且つその縮径によって前記スリーブ
１２の端部をそれぞれ締付け、スリーブ１２を前記スリ
ット１２ａの幅内で縮径させるものとなっている。即ち
、袋ナツト１３の外周に設けられたテーパ螺子１３ａは
、グリッド１４の螺子部に螺合し、そのねじ込み量に応
じて縮径して前記スリーブ１２の両端部をそれぞれ締め
込むものとなっている。この袋ナツト１３の全長は前記
スリーブ１２に比較してｙ！：１幅に設定されている。On the other hand, the cap nut 13 has an inner diameter larger than the outer diameter of the heat transfer tube 11, and tightens the ends of the sleeve 12 by reducing the diameter thereof, thereby reducing the diameter of the sleeve 12 within the width of the slit 12a. It has become a thing. That is, the tapered screw 13a provided on the outer periphery of the cap nut 13 is screwed into the threaded portion of the grid 14, and its diameter is reduced depending on the amount of screwing in, thereby tightening both ends of the sleeve 12, respectively. There is. The total length of this nut 13 is y compared to the sleeve 12! :Set to 1 width.
この結果、前記スリーブ１２は全体的には伝熱管１１の
曲率で湾曲しているが、その締め付は時の弾性変形によ
って上記袋ナツト１３との接触部は直管形状となり、強
固に取付は支持されるようになっている。As a result, the sleeve 12 as a whole is curved according to the curvature of the heat transfer tube 11, but due to elastic deformation during tightening, the contact portion with the cap nut 13 becomes a straight tube shape, making it difficult to securely attach the sleeve 12. It is gaining support.
しかして今、伝熱管１１にスリーブ１２を装着すると、
そのセルフアライメント性によってスリーブ１２は伝熱
管１１の所定の位置に嵌込まれる。そして、スリーブ１
２の両側にそれぞれ装着した袋ナツト１３をグリッド１
４にねじ込めば、前記テーパ螺子１３ａの作用によって
袋ナラ１−１３が縮径して前記スリラー７１２をその両
端で締め込むことになる。この締め込みによってスリー
ブ１２は前記スリット１２ａが形成した余裕空間の範囲
において弾性変形を呈して縮径し、その内面の全体を伝
熱管１１の外周面に接触させて伝熱管１１を支持するこ
とになる。この店果、伝熱管１１は片当りをｊＵ来する
ことなく、全面接触してスリーブ１２に支持されること
になる。However, now when the sleeve 12 is attached to the heat exchanger tube 11,
Due to its self-alignment property, the sleeve 12 is fitted into a predetermined position of the heat exchanger tube 11. And sleeve 1
The bag nuts 13 attached to both sides of grid 1
4, the diameter of the cap nut 1-13 is reduced by the action of the taper screw 13a, thereby tightening the thriller 712 at both ends thereof. By this tightening, the sleeve 12 is elastically deformed and reduced in diameter within the margin space formed by the slit 12a, and the entire inner surface of the sleeve 12 is brought into contact with the outer peripheral surface of the heat exchanger tube 11 to support the heat exchanger tube 11. Become. As a result, the heat exchanger tube 11 is supported by the sleeve 12 in full contact with the sleeve 12 without causing uneven contact.
かくしてこのような伝熱管１１の支持１７ＩＳ造によれ
ば、例えばプラントの起動または停止時や負荷変動によ
って上記伝熱管１１の周囲をｉ７１すれるヘリウムガス
等の熱媒体の温度が変化し、伝熱管１１に熱膨張が生じ
ても、伝熱管１１はスリーブ１２との閂で全面接触を保
ってすべることになる。また流体振動に対してもその支
持部が固定端として作用するので、所謂ガタを発生する
ことがない。故に支持部の摩擦を小さく抑え、且つ伝熱
管１１を安定に支持することが可能となるので、その異
常摩耗の発生を効果的に抑えることが可能となる。また
支持部のガタがない為に繰返したっきが生じ難く、セラ
ミック溶射部１２ｃの疲労クラックの発生を招く虞れも
なくなる。従って、伝熱管１１を安全性良く安定に支持
することが可能となり、また簡易な溝底なので実用性が
高い等の効果が奏せられる。Thus, according to the support structure 17IS for the heat transfer tubes 11, the temperature of the heat medium such as helium gas passing around the heat transfer tubes 11 changes due to, for example, startup or shutdown of the plant or load fluctuation, and the heat transfer tubes Even if thermal expansion occurs in the heat exchanger tube 11, the heat exchanger tube 11 will slide with the sleeve 12 in full contact with the bolt. Further, since the support portion acts as a fixed end against fluid vibration, so-called backlash does not occur. Therefore, it is possible to suppress the friction of the support portion to a low level and to stably support the heat exchanger tubes 11, so that the occurrence of abnormal wear can be effectively suppressed. Further, since there is no backlash in the support portion, repeated cracking is less likely to occur, and there is no risk of fatigue cracks occurring in the ceramic sprayed portion 12c. Therefore, it is possible to support the heat exchanger tube 11 safely and stably, and since the groove bottom is simple, it is highly practical.
尚、本発明は上述した実施例に限定されるものではない
。例えばスリーブ１２に設けるグループ１２ｃの数はそ
の使用に応じて定めれば良いものである。またスリーブ
１２の端部にビン穴１２ｄを設け、このビン穴１２ｄに
ビン（図示せず）を嵌込んでスリーブ１２の内径を拡大
してスリーブ１２を伝熱管１１に′ｆ：、着するように
すれば、その装着作業の容易化を図ることが可能となる
。その他、本発明はその要旨な逸説しない範囲で種々変
形して実船することかできる。Note that the present invention is not limited to the embodiments described above. For example, the number of groups 12c provided on the sleeve 12 may be determined depending on its use. Further, a bottle hole 12d is provided at the end of the sleeve 12, and a bottle (not shown) is fitted into the bottle hole 12d to enlarge the inner diameter of the sleeve 12 and attach the sleeve 12 to the heat transfer tube 11. By doing so, it becomes possible to facilitate the installation work. In addition, the present invention can be modified in various ways without departing from its essence.
第１図は本発明の一実施例を示す伝熱管支持部の侮造図
、第２図および第３図はそれぞれの側面構成図、第４図
はスリーブの要部構造を示す図、第５図は従来（１１１
造を示す図である。
１１・・伝熱筐、１２・・・スリーブ、１２ａ・・・ス
リット、１２ｂ・・・グループ（１１ろ） 、１２ｃ・
・・セラミック溶射部、１２ｄ ・・ビン穴、１３・
・・袋ナツト、１３ａ・・・テーパ螺子、１４・・・グ
リッド。
出願人復代理人 弁理士 鈴江武彦
第１図
第２図 第３図
１１ 第４図Fig. 1 is a simplified diagram of a heat exchanger tube support part showing one embodiment of the present invention, Figs. 2 and 3 are respective side configuration diagrams, Fig. 4 is a diagram showing the main structure of the sleeve, The figure is conventional (111
FIG. 11...Heat transfer case, 12...Sleeve, 12a...Slit, 12b...Group (11ro), 12c...
・・Ceramic sprayed part, 12d ・・Bottle hole, 13・
... Bag nut, 13a... Taper screw, 14... Grid. Applicant Sub-Agent Patent Attorney Takehiko Suzue Figure 1 Figure 2 Figure 3 11 Figure 4
Claims (1)
たスリーブを上記伝熱管を囲繞して設け、外周にテーパ
螺子を有し、グリッドにねじ込まれて縮径する袋ナット
により上記スリーブの両端をそれぞれ締付けて前記伝熱
管を上記スリーブを介して前記グリッドに固定支持して
なることを特徴とする伝熱管支持機構。A sleeve having the same curvature as the heat exchanger tube and having a slit in the axial direction is provided to surround the heat exchanger tube, and has a tapered screw on the outer periphery, and a cap nut that is screwed into the grid to reduce the diameter of the sleeve. A heat exchanger tube support mechanism characterized in that the heat exchanger tube is fixedly supported on the grid via the sleeve by tightening both ends.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16998084A JPS6149997A (en) | 1984-08-16 | 1984-08-16 | Heat transfer tube supporting mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16998084A JPS6149997A (en) | 1984-08-16 | 1984-08-16 | Heat transfer tube supporting mechanism |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS6149997A true JPS6149997A (en) | 1986-03-12 |
Family
ID=15896365
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP16998084A Pending JPS6149997A (en) | 1984-08-16 | 1984-08-16 | Heat transfer tube supporting mechanism |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6149997A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0477880U (en) * | 1990-11-13 | 1992-07-07 | ||
| US5297307A (en) * | 1993-04-16 | 1994-03-29 | Goldstar Co., Ltd. | Washing machine and method of controlling such |
-
1984
- 1984-08-16 JP JP16998084A patent/JPS6149997A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0477880U (en) * | 1990-11-13 | 1992-07-07 | ||
| US5297307A (en) * | 1993-04-16 | 1994-03-29 | Goldstar Co., Ltd. | Washing machine and method of controlling such |
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