JPH0437279Y2 - - Google Patents
Info
- Publication number
- JPH0437279Y2 JPH0437279Y2 JP19927584U JP19927584U JPH0437279Y2 JP H0437279 Y2 JPH0437279 Y2 JP H0437279Y2 JP 19927584 U JP19927584 U JP 19927584U JP 19927584 U JP19927584 U JP 19927584U JP H0437279 Y2 JPH0437279 Y2 JP H0437279Y2
- Authority
- JP
- Japan
- Prior art keywords
- impeller
- tongue
- reference line
- discharge
- casing
- 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
- 230000003068 static effect Effects 0.000 description 17
- 238000010586 diagram Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 5
- 230000001629 suppression Effects 0.000 description 1
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
- Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
Description
【考案の詳細な説明】
（産業上の利用分野）
本考案は、空気調和機に使用する横流れフアン
に係り、特に静圧が高くかつ運転音の低減を計つ
た横流れフアンに関する。[Detailed Description of the Invention] (Industrial Application Field) The present invention relates to a cross-flow fan used in an air conditioner, and particularly to a cross-flow fan that has high static pressure and reduces operating noise.
（従来の技術）
最近の空気調和機、特にその室内機についてみ
れば、室内インテリア性を重視するユーザのニー
ズを反映して、空気調和機を目立たない形態とす
る方向の努力がはらわれてきている。ところが、
従来の空気調和機の壁掛形室内機についてみれ
ば、送風用フアンの流れパターンからみて、第７
図に示す如く、正面上方に大きい開孔部を有する
吸込グリル２０′が、その下に若干のフラツト壁
２１′を挟んで吹出グリル２２′が正面下部に開口
されており、横流れフアン２３′が見えているが、
上記ユーザの室内インテリア性重視からみて、第
２図図示の如く、正面上方に比較的小さい吸込グ
リル２０を開口させ、その下方はフラツト壁２１
に置換え、吹出グリル２２は正面に垂直な底部に
開口させ、横流れフアン２３は正面から見えない
形態のものが望まれている。(Prior Art) Looking at recent air conditioners, especially their indoor units, efforts have been made to make the air conditioners less conspicuous, reflecting the needs of users who place importance on interior design. There is. However,
Looking at the wall-mounted indoor unit of a conventional air conditioner, the 7th
As shown in the figure, there is a suction grill 20' with a large opening in the upper front, and below that, an outlet grill 22' is opened in the lower front with a flat wall 21' in between, and a lateral flow fan 23' is installed. I can see it, but
In view of the user's emphasis on interior design, as shown in FIG.
It is desired that the blow-out grille 22 be opened at the bottom perpendicular to the front, and that the lateral flow fan 23 be invisible from the front.
本考案はかかる空気調和機の動向を踏まえ、そ
の形態にマツチする横流れフアンを供給せんとす
るもので、その流れパターンとしては、1959年ス
イス、ケスター氏がその学位論文で公表したもの
や、特開昭59−34498号公報のものが知られてい
るが、いずれも昇圧用としては満足できるも、運
転音の面では考慮されていないので、空気調和機
としてその形態をそのまま用いるには問題があ
る。 The present invention is based on the trend of air conditioners, and aims to provide a cross-flow fan that matches the shape of the air conditioner. The one published in 1983-34498 is known, but although all of them are satisfactory for pressure boosting, they do not take into consideration the operational noise, so there is a problem in using that form as it is as an air conditioner. be.
（考案が解決しようとする問題点）
そこで本考案は、前記の如き室内インテリアに
マツチする横流れフアンであり、静圧が大きく、
かつ運転音を低くすることを目的とするものであ
る。(Problems to be Solved by the Invention) Therefore, the present invention is a horizontal flow fan that is suitable for indoor interiors as described above, and has a large static pressure.
The purpose is also to reduce operating noise.
（問題点を解決するための手段および作用）
そこで本考案は、横流れフアンを、円筒状の羽
根車と、羽根車の円筒面を包設するケーシング前
板およびケーシング後板とで構成し、ケーシング
前板およびケーシング後板の形状を実用新案登録
請求の範囲に記載のとおりの、最適のものとなす
ことにより、静圧が十分大きく、かつ運転音の低
減を計つたものである。(Means and effects for solving the problem) Therefore, the present invention consists of a lateral flow fan including a cylindrical impeller, a casing front plate and a casing rear plate that enclose the cylindrical surface of the impeller, and the casing By optimizing the shapes of the front plate and the rear plate of the casing as described in the claims of the utility model registration, static pressure is sufficiently large and driving noise is reduced.
（実施例）
以下本考案を第１図ないし第６図に示す一実施
例に基づいて詳細に説明する。(Embodiment) The present invention will be described in detail below based on an embodiment shown in FIGS. 1 to 6.
第１図において、横流れフアンを円筒状の羽根
車１と、羽根車１の円筒面を包設するケーシング
前板３およびケーシング後板４とで構成してい
る。ケーシング後板４の形状は吸込領域１５に設
けた吸込案内部５を羽根車１の中心２を通り風上
側に延びる基準線２ａとほぼ平行にし、風下の羽
根車１と最も距離の近い舌部６を中心２と結ぶ直
線が前記基準線２ａとなす角度θB1が ０＜θB1＜
90°になる如くし、また、さらに風下の吐出案内
部７は羽根車１の外周との距離h1が風下側に向つ
て拡大する如く形成する。 In FIG. 1, the crossflow fan is composed of a cylindrical impeller 1, and a casing front plate 3 and a casing rear plate 4 that enclose the cylindrical surface of the impeller 1. The shape of the casing rear plate 4 is such that the suction guide portion 5 provided in the suction region 15 is approximately parallel to the reference line 2a that passes through the center 2 of the impeller 1 and extends to the windward side, and the tongue portion closest to the leeward impeller 1 is formed. The angle θ B1 between the straight line connecting 6 to the center 2 and the reference line 2a is 0<θ B1 <
Further, the discharge guide section 7 on the leeward side is formed so that the distance h1 from the outer periphery of the impeller 1 increases toward the leeward side.
一方、ケーシング前板３の形状は吸込領域１５
に設けた吸込案内部８を前記基準線２ａとほぼ平
行とし、かつ基準線２ａからの距離L1を羽根車
１の直径をＤとしたとき、L1＞0.75D
とし、風下の羽根車１の外周と最も距離の近い舌
部９との間を曲線状に形成する。そして、舌部９
は中心２と結ぶ直線が基準線２ａとなす角度θF1
を、
75°＜θF1＜105°になる如くし、さらに風下の舌
部案内部１０はその終点の舌部案内部終点１１ま
では、羽根車１の外周との間隔h2が風下側に向つ
て拡大する如く形成し、さらに風下の吐出案内部
１２は前記ケーシング後板４の吐出案内部７とほ
ぼ平行となる如く形成し、吐出案内部１２の吐出
端１４と吐出案内部７の吐出端１３とで形成され
る吐出口１６の幅 L2を、0.45D＜L2＜0.7D
とする。また、ケーシング後板４の吐出案内部
７と前記基準線２ａとの支点１７と羽根車１の中
心２との距離L3が前記羽根車１の直径Ｄとほぼ
等しくなる如く形成している。 On the other hand, the shape of the casing front plate 3 is
The suction guide section 8 provided at A curved line is formed between the outer periphery of the tongue portion 9 and the tongue portion 9 that is closest to the tongue portion 9 . And the tongue part 9
is the angle θ F1 between the straight line connecting center 2 and reference line 2a
, so that 75°<θ F1 <105°, and further, the distance h 2 from the outer circumference of the impeller 1 to the tongue guide end point 11 of the leeward tongue guide section 10 is set to the leeward side. Furthermore, the discharge guide section 12 on the leeward side is formed so as to be substantially parallel to the discharge guide section 7 of the casing rear plate 4, and the discharge end 14 of the discharge guide section 12 and the discharge guide section 7 The width L 2 of the discharge port 16 formed with the end 13 is 0.45D<L 2 <0.7D. Further, the distance L3 between the fulcrum 17 between the discharge guide portion 7 of the casing rear plate 4 and the reference line 2a and the center 2 of the impeller 1 is approximately equal to the diameter D of the impeller 1.
ここで、吐出案内部７の吐出端１３は前記基準
線２ａよりもケーシング前板３側に位置するとと
もに、吐出案内部１２の吐出端１４は吐出端１３
と対向する位置にある。 Here, the discharge end 13 of the discharge guide section 7 is located closer to the casing front plate 3 than the reference line 2a, and the discharge end 14 of the discharge guide section 12 is located at the discharge end 13.
It is located opposite to.
かくの如く構成した横流れフアンを、第２図に
示す如く空気調和機に組み込むものである。すな
わち、正面上方に比較的小さい吸込グリル２０を
開口させ、その下方はフラツト壁２１とし、吹出
グリル２２は正面から見えない底部に開口させ、
吸込グリル２０に対面させて熱交換器２４を、ま
たその風下側のフラツト壁２１の後方に横流れフ
アン２３をそれぞれ配設し、横流れフアン２３の
基準線２ａをフラツト壁２１に平行し、吹出口１
６を吹出グリル２２に対面させている。なお、羽
根車１は点線で示す如く時計方向に回転させるも
のである。 The transverse flow fan constructed as described above is incorporated into an air conditioner as shown in FIG. That is, a relatively small suction grill 20 is opened at the upper part of the front, a flat wall 21 is formed below the intake grill 20, and an outlet grill 22 is opened at the bottom where it cannot be seen from the front.
A heat exchanger 24 is disposed facing the suction grill 20, and a crossflow fan 23 is disposed behind the flat wall 21 on the leeward side of the heat exchanger 24, and the reference line 2a of the crossflow fan 23 is parallel to the flat wall 21, and the air outlet 1
6 is made to face the blow-off grill 22. Note that the impeller 1 is rotated clockwise as shown by the dotted line.
しかして、前記したケーシング後板４の舌部６
が基準線２ａとのなす角度θB1、ケーシング前板
３の吸込案内部８と基準線２ａとの距離L1、舌
部９と中心２とを結ぶ直線が基準線２ａとなす角
度θF1、および吐出口１６の幅L2のそれぞれの値
は、本考案横流れフアンが十分な静圧を有しかつ
低騒音となるために最適の形状を実験的に求めた
ものであり、以下にその詳細を説明する。 Therefore, the tongue portion 6 of the casing rear plate 4 described above
is the angle θ B1 formed by the reference line 2a, the distance L 1 between the suction guide part 8 of the casing front plate 3 and the reference line 2a, the angle θ F1 made by the straight line connecting the tongue part 9 and the center 2 with the reference line 2a, The respective values of the width L 2 of the discharge port 16 were determined experimentally to determine the optimal shape for the cross-flow fan of the present invention to have sufficient static pressure and low noise.The details are as follows. Explain.
先ず、ケーシング後板４の舌部６の位置、すな
わち、羽根車１の中心２と舌部６とを結ぶ直線が
基準線２ａとなす角θB1は、0°より小さくなると、
吸込面積が小さくなりすぎ、第３図に示す如く得
られる静圧PSが小さくなり、運転音が高くなる。
また、90°以上になると吸込面積が大き過ぎ性能
が低下するので、θB1としては0°と90°の間の値で
あることが望ましいものである。 First, when the position of the tongue portion 6 of the casing rear plate 4, that is, the angle θ B1 between the straight line connecting the center 2 of the impeller 1 and the tongue portion 6 and the reference line 2a, becomes smaller than 0°,
The suction area becomes too small, and as shown in FIG. 3, the obtained static pressure P S becomes small and the operating noise becomes high.
Further, if it exceeds 90°, the suction area becomes too large and the performance deteriorates, so it is desirable that θ B1 has a value between 0° and 90°.
次に、ケーシング前板３の吸込案内部８と基準
線２ａとの距離L1が小さすぎると、空気はスム
ーズに流入できなくなり、特に、通常流速が大
で、空気に対して大きな仕事を与える舌部９近辺
の吸込領域１５の運転音LAの増大につながる。
ある程度以上（すなわち羽根車１の直径をＤとし
たときL1＞0.75D以上、第４図参照）であれば、
十分な効果が得られ、制圧PSも高くできるもので
ある。 Next, if the distance L 1 between the suction guide section 8 of the casing front plate 3 and the reference line 2a is too small, the air will not be able to flow in smoothly, especially when the normal flow velocity is high and a large amount of work will be applied to the air. This leads to an increase in the operating noise L A in the suction region 15 near the tongue portion 9 .
If it is more than a certain level (i.e., when the diameter of the impeller 1 is D, L 1 >0.75D or more, see Figure 4),
A sufficient effect can be obtained, and the suppression PS can also be increased.
更に、ケーシング前板３の舌部９の位置、すな
わち、羽根車１の中心２と舌部９とを結ぶ直線が
基準線２ａとなす角θF1は、第５図に示す如く、
角θF1が小さすぎると、運転音LAが低いものの、
静圧PSが低くなる。反対に、角θF1が大きすぎる
と、得られる静圧PSは余り変化しないが、運転音
LAが急激に増大した実用に耐えないものである。
この理由を以下に説明する。 Furthermore, the position of the tongue 9 of the casing front plate 3, that is, the angle θ F1 between the straight line connecting the center 2 of the impeller 1 and the tongue 9 with the reference line 2a, is as shown in FIG.
If the angle θ F1 is too small, although the operating noise L A is low,
Static pressure P S becomes lower. On the other hand, if the angle θ F1 is too large, the resulting static pressure P S will not change much, but the operating noise will increase.
The L A has increased rapidly and cannot be put into practical use.
The reason for this will be explained below.
一般に用いられている横流れフアンでは角θF1
を大きくする（すなわち舌部案内部１０を小さく
する）と、静圧が高くなつて、運転音も大きくな
るが、本考案の横流れフアンでは、通常流速が大
で、空気に対し大きな仕事を与える領域であるケ
ーシング前板３の舌部９付近の流速が、ケーシン
グ前板３の吸込案内部８の存在のために小さくな
り、空気に対して大きな仕事を与えることができ
なくなる。従つて、角θF1は第５図に示す如く、
運転音LAも小さく静圧PSも十分ある 75°と105°
との間の値とすることが好ましい。 In commonly used cross-flow fans, the angle θ F1
Increasing (that is, reducing the size of the tongue guide portion 10) increases the static pressure and increases the operating noise.However, in the cross flow fan of the present invention, the flow velocity is usually high and a large amount of work is applied to the air. The flow velocity near the tongue portion 9 of the casing front plate 3 becomes small due to the presence of the suction guide portion 8 of the casing front plate 3, and it becomes impossible to apply a large amount of work to the air. Therefore, the angle θ F1 is as shown in FIG.
Operating noise L A is small and static pressure P S is sufficient 75° and 105°
It is preferable to take a value between .
更に、吐出口１６の幅L2に関しては、L2が羽
根車１の直径Ｄに比して大き過ぎると、吐出口１
６より吐出された流速が急激な減速される結果、
サージングが発生して不安定性能になり、得られ
る静圧が低く、運転音が高くなり実用に供し得な
い。また、L2が小さ過ぎると、安定性能が得ら
れ運転音が低くなるが、デイフユーザ効果が得ら
れず静圧が上昇しないので、実用に供し得ない。
このL2とＤとの関係は第６図に示す如くであり、
L2の好ましい値としては 0.45D＜L2＜0.7Dとな
るものである。 Furthermore, regarding the width L 2 of the discharge port 16, if L 2 is too large compared to the diameter D of the impeller 1, the discharge port 1
As a result of the rapid deceleration of the flow velocity discharged from 6,
Surging occurs, leading to unstable performance, resulting in low static pressure and high operating noise, making it unsuitable for practical use. On the other hand, if L 2 is too small, stable performance will be obtained and the operating noise will be reduced, but the differential user effect will not be obtained and the static pressure will not increase, making it impossible to put it to practical use.
The relationship between L 2 and D is as shown in Figure 6,
A preferable value for L 2 is 0.45D<L 2 <0.7D.
また、ケーシング後板４の吐出案内部７は、前
記の如き各角度および距離の設定による高静圧化
を有効に図るためこの吐出案内部７と基準線２ａ
との交点１７と羽根車１の中心２との距離L3を、
羽根車１の直径Ｄとほぼ等しくなるよう形成す
る。 Further, the discharge guide part 7 of the casing rear plate 4 is connected to the reference line 2a in order to effectively increase the static pressure by setting each angle and distance as described above.
The distance L 3 between the intersection 17 and the center 2 of the impeller 1 is
It is formed to be approximately equal to the diameter D of the impeller 1.
これは、L3が羽根車１の直径Ｄに比して大き
過ぎると、吐出案内部７付近の気流の絶対速度の
方向が羽根車１の回転方向に対してすべり、その
周方向成分が小さくなり、羽根車１が気流に与え
るエネルギーが小さくなり圧力損失が大きくなる
結果高静圧が得られないためである。また、L3
が羽根車１の直径Ｄに比して小さ過ぎると、ケー
シング後板４は羽根車１との間の空間の拡大率が
小さくなり、羽根車１から吐出される気流の風速
が大きくなり高動圧が得られるものの、気流の速
度変化が抑えられてデイフエーザ効果が働かない
結果高静圧が得られないためである。 This is because if L3 is too large compared to the diameter D of the impeller 1, the direction of the absolute velocity of the airflow near the discharge guide section 7 will slip with respect to the rotation direction of the impeller 1, and its circumferential component will be small. This is because the impeller 1 gives less energy to the airflow and pressure loss increases, making it impossible to obtain high static pressure. Also, L 3
If the diameter D is too small compared to the diameter D of the impeller 1, the expansion rate of the space between the casing rear plate 4 and the impeller 1 will be small, and the wind speed of the airflow discharged from the impeller 1 will increase, resulting in high movement. This is because although pressure can be obtained, high static pressure cannot be obtained as a result of suppressed changes in airflow velocity and the diffuser effect does not work.
（考案の効果）
本考案は叙述の如く、ケーシング後板の舌部が
基準線となす角度θB1、ケーシング前板の吸込案
内部と基準線との距離L1、舌部と中心とを結ぶ
直線が基準線となす角度θF1、吐出口の幅L2およ
びケーシング後板の吐出案内部と基準線との交点
と羽根車の中心との距離L3のそれぞれの角度ま
たは寸法について最適の値を実験的に求めたの
で、静圧が十分高くしかも運転音の低い高性能の
横流れフアンを提供できるものである。(Effect of the invention) As described above, the present invention is based on the angle θ B1 that the tongue of the casing rear plate makes with the reference line, the distance L 1 between the suction guide part of the casing front plate and the reference line, and the connection between the tongue and the center. Optimal values for the angle θ F1 between the straight line and the reference line, the width L 2 of the discharge port, and the distance L 3 between the intersection of the discharge guide on the casing rear plate and the reference line and the center of the impeller. was determined experimentally, so it is possible to provide a high-performance cross-flow fan with sufficiently high static pressure and low operating noise.
第１図および第２図は本考案横流れフアンの一
実施例を示す図であり、第１図はその詳細説明
図、第２図は本考案横流れフアンを組込んだ空気
調和機の空内機の概略図、第３図および第５図は
本考案横流れフアンのケーシング後板および前板
の基準線とのなす角度θB1およびθF1と静圧および
運転音との特性を示す図、第４図および第６図は
ケーシング前板の吸込案内部と基準線との距離
L1および吐出口の幅L2と羽根車の直径Ｄとの比
と静圧および運転音との関係を示す特性図、第７
図は従来の横流れフアンを組込んだ空気調和機の
室内機の概略図である。
１……羽根車、２……中心、２ａ……基準線、
３……ケーシング前板、４……ケーシング後板、
５，８……吸込案内部、６，９……舌部、７，１
２……吐出案内部、１０……舌部案内部、１１…
…舌部案内部終点、１３，１４……吐出端、１６
……吐出口。
Figures 1 and 2 are diagrams showing one embodiment of the cross-flow fan of the present invention, with Figure 1 being a detailed explanatory diagram thereof, and Figure 2 being an air conditioner incorporating the cross-flow fan of the present invention. 3 and 5 are diagrams showing the characteristics of angles θ B1 and θ F1 between the reference line of the rear plate and front plate of the casing of the cross-flow fan of the present invention, static pressure, and operating noise. Figures and Figure 6 show the distance between the suction guide section of the casing front plate and the reference line.
Characteristic diagram showing the relationship between the ratio of L 1 and the discharge port width L 2 to the impeller diameter D, static pressure, and operation noise, 7th
The figure is a schematic diagram of an indoor unit of an air conditioner incorporating a conventional cross-flow fan. 1... impeller, 2... center, 2a... reference line,
3... Casing front plate, 4... Casing rear plate,
5, 8... Suction guide part, 6, 9... Tongue part, 7, 1
2... Discharge guide section, 10... Tongue guide section, 11...
...Tongue guide end point, 13, 14...Discharge end, 16
...Discharge port.
Claims (1)
するケーシング前板３およびケーシング後板４と
で構成され、前記ケーシング後板４は吸込案内部
５、舌部６、吐出案内部７より形成され、前記吸
込案内部５は羽根車１の中心２を通る基準線２ａ
とほぼ平行に、前記舌部６は中心２と結ぶ直線が
前記基準線２ａとなす角度θB1が０＜θB1＜90°にな
る如く、また吐出案内部７は羽根車１の外周との
間隔h1が風下側に向つて拡大する如くそれぞれ形
成するとともに、ケーシング前板３は吸込案内部
８、舌部９、舌部案内部１０、舌部案内部終点１
１、吐出案内部１２より形成され、前記吸込案内
部８は前記基準線２ａとほぼ平行でかつ基準線２
ａとの距離L1を羽根車１の直径ＤのL1＞0.75Dと
し、舌部９は中心２と結ぶ直線が基準線２ａとな
す角度θF1が、75°＜θF1＜105°になる如く、また舌
部案内部１０は羽根車１の外周との間隔h2が風下
側に向つて拡大する如く形成し、かつ前記基準線
２ａよりもケーシング前板３側に位置する前記ケ
ーシング後板４の吐出端１３と、吐出端１３と対
向する位置にあるケーシング前板３の吐出端１４
とで形成される吐出口１６の幅L2を、0.45D＜L2
＜0.7Dとするとともに、ケーシング後板４の吐
出案内部７と前記基準線２ａとの交点１７と羽根
車１の中心との距離L3を前記羽根車１の直径Ｄ
とほぼ等しくなしたことを特徴とする横流れフア
ン。 It is composed of a cylindrical impeller 1, a casing front plate 3 and a casing rear plate 4 that enclose the cylindrical surface of the impeller 1, and the casing rear plate 4 has a suction guide section 5, a tongue section 6, and a discharge guide section. 7, and the suction guide portion 5 is formed from a reference line 2a passing through the center 2 of the impeller 1.
The tongue part 6 is arranged so that the angle θ B1 between the straight line connected to the center 2 and the reference line 2a is 0<θ B1 <90°, and the discharge guide part 7 is arranged almost parallel to the outer periphery of the impeller 1. The casing front plate 3 has a suction guide portion 8, a tongue portion 9, a tongue portion guide portion 10, and a tongue portion guide end point 1.
1. It is formed of a discharge guide section 12, and the suction guide section 8 is approximately parallel to the reference line 2a and is parallel to the reference line 2a.
The distance L 1 from the impeller 1 to the diameter D of the impeller 1 is L 1 >0.75D, and the angle θ F1 between the straight line connecting the tongue portion 9 and the center 2 and the reference line 2a is 75° < θ F1 < 105°. In addition, the tongue guide portion 10 is formed such that the distance h2 from the outer periphery of the impeller 1 increases toward the leeward side, and the tongue guide portion 10 is formed so that the distance h2 from the outer periphery of the impeller 1 increases toward the leeward side, and A discharge end 13 of the plate 4 and a discharge end 14 of the casing front plate 3 located at a position opposite to the discharge end 13.
The width L 2 of the discharge port 16 formed by 0.45D<L 2
<0.7D, and the distance L3 between the intersection 17 of the discharge guide portion 7 of the casing rear plate 4 and the reference line 2a and the center of the impeller 1 is the diameter D of the impeller 1.
A lateral flow fan characterized by being approximately equal to.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19927584U JPH0437279Y2 (en) | 1984-12-25 | 1984-12-25 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19927584U JPH0437279Y2 (en) | 1984-12-25 | 1984-12-25 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS61110891U JPS61110891U (en) | 1986-07-14 |
| JPH0437279Y2 true JPH0437279Y2 (en) | 1992-09-02 |
Family
ID=30759048
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP19927584U Expired JPH0437279Y2 (en) | 1984-12-25 | 1984-12-25 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0437279Y2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2517545Y2 (en) * | 1989-05-24 | 1996-11-20 | ダイキン工業株式会社 | Air conditioner |
-
1984
- 1984-12-25 JP JP19927584U patent/JPH0437279Y2/ja not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS61110891U (en) | 1986-07-14 |
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