JPH05637B2 - - Google Patents
Info
- Publication number
- JPH05637B2 JPH05637B2 JP9503884A JP9503884A JPH05637B2 JP H05637 B2 JPH05637 B2 JP H05637B2 JP 9503884 A JP9503884 A JP 9503884A JP 9503884 A JP9503884 A JP 9503884A JP H05637 B2 JPH05637 B2 JP H05637B2
- Authority
- JP
- Japan
- Prior art keywords
- plate
- blade
- sealing material
- heat exchange
- outer circumferential
- 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 - Lifetime
Links
- 238000005192 partition Methods 0.000 claims description 15
- 239000000463 material Substances 0.000 claims description 10
- 239000003566 sealing material Substances 0.000 description 24
- 238000001816 cooling Methods 0.000 description 8
- 238000001035 drying Methods 0.000 description 7
- 230000002093 peripheral effect Effects 0.000 description 6
- 230000000694 effects Effects 0.000 description 3
- 239000000203 mixture Substances 0.000 description 3
- 238000009423 ventilation Methods 0.000 description 3
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 3
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 2
- 229910052782 aluminium Inorganic materials 0.000 description 2
- 239000011347 resin Substances 0.000 description 2
- 229920005989 resin Polymers 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 229910001220 stainless steel Inorganic materials 0.000 description 2
- 239000010935 stainless steel Substances 0.000 description 2
- 238000007664 blowing Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D19/00—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium
- F28D19/04—Regenerative heat-exchange apparatus in which the intermediate heat-transfer medium or body is moved successively into contact with each heat-exchange medium using rigid bodies, e.g. mounted on a movable carrier
- F28D19/047—Sealing means
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Description
【発明の詳細な説明】
産業上の利用分野
本発明は波形状薄板からなるブレードを有し、
このブレードの両面でそれぞれ温度の異なる空気
の送風機能をもつと同時にブレードを介して温度
の異なる空気間で熱交換をも行なうことのできる
熱交換型送風機に関するものである。DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention has a blade made of a corrugated thin plate,
This invention relates to a heat exchange type blower which has the function of blowing air having different temperatures on both sides of the blade, and at the same time can exchange heat between air having different temperatures through the blade.
従来例の構成とその問題点
第１図は従来の熱交換送風機のインペラ部分を
示し、１はステンレス、アルミニウム、樹脂等の
波形状薄板で構成されるブレード、２はブレード
１を回転中心側から支持しかつ回転軸にインペラ
を固定するためのボス３を有する主板である。４
はブレード１を主板２と共に外周方向から支持す
る外周板で、その外周には略リング状で断面略Ｖ
字型の可撓性を有するシール材５が固定してあ
る。第２図は上記インペラを第１のケーシング
６、第２のケーシング７に組込んだ概略断面構造
を示し、８はブレード１の両面の空気流れを分離
する仕切板、９は前記シール材５が摺動する摺動
材である。第１のケーシング６側の空気流れを
９、第２のケーシング７側の空気流れを１０とす
ると、インペラが回転すると空気流れ９，１０は
ブレード１を介して熱交換することになる。Configuration of conventional example and its problems Figure 1 shows the impeller part of a conventional heat exchange blower, in which 1 is a blade made of a corrugated thin plate made of stainless steel, aluminum, resin, etc., and 2 is blade 1 from the rotation center side. This is a main plate having a boss 3 for supporting and fixing the impeller to the rotating shaft. 4
is an outer circumferential plate that supports the blade 1 together with the main plate 2 from the outer circumferential direction, and the outer circumference has a substantially ring-shaped cross section of approximately V.
A flexible sealing material 5 in the shape of a letter is fixed. FIG. 2 shows a schematic cross-sectional structure in which the impeller is assembled into a first casing 6 and a second casing 7, in which 8 is a partition plate that separates the air flow on both sides of the blade 1, and 9 is a partition plate that separates the air flow on both sides of the blade 1. It is a sliding material that slides. Assuming that the air flow on the first casing 6 side is 9 and the air flow on the second casing 7 side is 10, the air flows 9 and 10 will exchange heat via the blades 1 when the impeller rotates.
前記シール材５は第３図のように仕切板８に固
定された略リング状の摺動材９がシール材５の断
面略Ｖ字型の中央に位置するように取付けられて
おり、インペラが回転すると、その遠心力および
風力によりシール材５が摺動材９に摺動し、外周
板４と仕切板８の隙間をシールしていた。 The sealing material 5 is installed so that the substantially ring-shaped sliding material 9 fixed to the partition plate 8 is located at the center of the substantially V-shaped cross section of the sealing material 5, as shown in FIG. When rotated, the centrifugal force and wind force caused the sealing material 5 to slide on the sliding material 9, sealing the gap between the outer peripheral plate 4 and the partition plate 8.
上記構成においては、第１のフアンケーシング
６側と第２のフアンケーシング７側の負荷が異な
ると、その圧力PA，PBが異なり、例えばPA＞PB
となつた場合、シール材５は摺動材９のａ部に、
ｂ部より強く押圧され、回転トルクが増大すると
ともに、前記シール材５の耐摩耗性に問題があつ
た。また、シール材５の摺動材９への押圧力がａ
部とｂ部で異なる為、空気流９，１０が混流し、
熱交換効率の低下をまねくといつた問題があつ
た。 In the above configuration, if the loads on the first fan casing 6 side and the second fan casing 7 side are different, the pressures P A and P B will be different, for example, P A > P B
In this case, the sealing material 5 is placed on the a part of the sliding material 9,
The seal material 5 was pressed more strongly than the b portion, and the rotational torque increased, and the wear resistance of the sealing material 5 was problematic. Also, the pressing force of the sealing material 5 on the sliding material 9 is a
Since the airflows 9 and 10 are different between part and b, the airflows 9 and 10 mix,
There was a problem that led to a decrease in heat exchange efficiency.
発明の目的
本発明の熱交換型送風機はこのような従来の問
題点を解消し、回転トルクの軽減と耐久性の向上
および熱交換効率の安定をはかつた熱交換型送風
機を提供するものである。Purpose of the Invention The heat exchange type blower of the present invention solves these conventional problems, and provides a heat exchange type blower that reduces rotational torque, improves durability, and stabilizes heat exchange efficiency. be.
発明の構成
本発明の熱交換型送風機は、ブレードと外周板
と仕切板を備え、前記外周板には略リング状で断
面略Ｖ字型の可撓性を有するシール材を固定し、
前記仕切板は、その摺動部を前記シール材の断面
略Ｖ字型の中央に位置させ、かつこの摺動部を前
後方向に揺動自在としたものであり、熱交換型送
風機が回転し仕切板の両側の圧力が異なつた場合
でも、前記摺動部は常にシール材の断面略Ｖ字型
の中央に位置し、回転時のシール材と摺動部の摺
動抵抗を小さくでき、回転トルクの軽減とシール
材の耐久性の向上がはかれるものである。Structure of the Invention The heat exchange type blower of the present invention includes a blade, an outer peripheral plate, and a partition plate, and a flexible sealing material having a substantially ring shape and a substantially V-shaped cross section is fixed to the outer peripheral plate,
The partition plate has a sliding portion located at the center of the substantially V-shaped cross section of the sealing material, and is swingable in the front and rear directions, so that the heat exchange type blower rotates. Even if the pressure on both sides of the partition plate is different, the sliding part is always located at the center of the approximately V-shaped cross section of the sealing material, and the sliding resistance between the sealing material and the sliding part during rotation can be reduced. This reduces torque and improves the durability of the sealing material.
また、シール材と仕切板とのシール性は仕切板
の摺動部の両側において、略均一であり、ブレー
ド両面の溝部分を流れる２種類の空気流は混流す
ることなく、熱交換効率の向上がはかれるもので
ある。 In addition, the sealing performance between the sealing material and the partition plate is almost uniform on both sides of the sliding part of the partition plate, and the two types of air flows flowing through the grooves on both sides of the blade do not mix, improving heat exchange efficiency. It is something that can be measured.
実施例の説明
以下、添付図面に基づいて本発明の一実施例に
ついて説明する。DESCRIPTION OF EMBODIMENTS An embodiment of the present invention will be described below with reference to the accompanying drawings.
第４図は熱交換型送風機のインペラ部分を示
し、１１はステンレス、アルミニウム、樹脂等の
波形状薄板で構成されるブレード、１２はブレー
ド１１を回転中心側から支持しかつ固定するため
のボス１３を有する主板である。 FIG. 4 shows the impeller part of a heat exchange type blower, where 11 is a blade made of a corrugated thin plate made of stainless steel, aluminum, resin, etc., and 12 is a boss 13 for supporting and fixing the blade 11 from the rotation center side. The main plate has a
１４はブレード１１を主板１２と共に外周方向
から支持する略リング状の外周板である。 Reference numeral 14 denotes a substantially ring-shaped outer circumferential plate that supports the blade 11 together with the main plate 12 from the outer circumferential direction.
１５は外周板１４の外周部に固定された略リン
グ状で断面略Ｖ字型の可撓性を有するシール材で
ある。 Reference numeral 15 denotes a flexible sealing material having a substantially ring shape and a substantially V-shaped cross section, which is fixed to the outer peripheral portion of the outer circumferential plate 14 .
第５図は、上記インペラを組込んだ衣類乾燥機
の概略断面構造を示し、１６は乾燥機の外枠、１
７は外枠１６内に回転自在に設置したドラム、１
８はドラム１７内に被乾燥物を投入するためのド
ア、１９は第４図に示したインペラ、２０はイン
ペラ１９を回転させる回転軸で、主板１２のボス
１３に固定してある。 FIG. 5 shows a schematic cross-sectional structure of a clothes dryer incorporating the above-mentioned impeller, where 16 is an outer frame of the dryer, 1
7 is a drum rotatably installed within the outer frame 16;
Reference numeral 8 denotes a door for introducing the material to be dried into the drum 17, 19 the impeller shown in FIG. 4, and 20 a rotating shaft for rotating the impeller 19, which is fixed to the boss 13 of the main plate 12.
２１はインペラ１９を内包し通風路を形成する
ケーシング、２２はインペラ１９の両面の空気流
を通風路部分で仕切る仕切板で、外周板１４の外
周方向に位置する。２３は高温多湿な乾燥用循環
空気を導くためのダクトで途中にヒータ２４を設
けている。 21 is a casing that encloses the impeller 19 and forms a ventilation passage; 22 is a partition plate that partitions the air flow on both sides of the impeller 19 from the ventilation passage portion, and is located in the outer circumferential direction of the outer peripheral plate 14; 23 is a duct for guiding hot and humid drying circulating air, and a heater 24 is provided in the middle.
２５は吸気された冷却空気を排気するためのダ
クトである。２６，２７はそれぞれ乾燥用循環空
気、冷却空気の流れを示している。２８は除湿水
を機外に排出する排水口である。 25 is a duct for exhausting the intake cooling air. Reference numerals 26 and 27 indicate the flows of drying circulating air and cooling air, respectively. 28 is a drain port for discharging dehumidified water to the outside of the machine.
上記構成において、電源を入れてモータ（図示
せず）を回転させ、この回転力でインペラ１９を
回転させると、インペラ１９の両面で２つの異な
る空気流、すなわち、循環空気２６、冷却空気２
７の流れが発生する。乾燥用循環空気２６はヒー
タ２４で加熱された後にドラム１７に入り、ドラ
ム１７内の衣類を加熱した後にインペラ１９の一
方の面に沿つて移動し、ダクト２３を介し再びヒ
ータ２４方向に向かう。 In the above configuration, when the power is turned on and the motor (not shown) is rotated, and the impeller 19 is rotated by this rotational force, two different air flows are generated on both sides of the impeller 19, namely, circulating air 26 and cooling air 2.
7 flow occurs. The drying circulating air 26 enters the drum 17 after being heated by the heater 24, moves along one surface of the impeller 19 after heating the clothes in the drum 17, and heads toward the heater 24 again via the duct 23.
冷却空気２７は機外から吸込まれ、インペラ１
９の他方の面に沿つて移動し、ダクト２５を介し
再び機外へ出る。そして、両空気はブレード１１
の両面溝部分を薄板１枚を間に挾んで隣り合つて
流れ、この時、温度の高い乾燥用循環空気２６か
ら温度の低い冷却空気２７へとブレード１１を介
して熱が移動し、循環空気２６は冷却され、これ
に含まれている水分は凝結し、水滴となり排水口
２８より排水され、乾燥用循環空気２５は除湿さ
れる。除湿された乾燥用循環空気２６はインペラ
１９とケーシング２１及び仕切板２２とで構成さ
れる通風路を通り、循環用ダクト２２を通りヒー
タ２４部分を通り、ここで加熱されドラム１７に
もどるという循環を行なう。一方、冷却空気２７
は機外より吸入され、インペラ１９内に入りここ
で乾燥用循環空気２６を冷却し、排気ダクト２５
より機外へ排気される。 Cooling air 27 is sucked in from outside the machine, and the impeller 1
9 and exits the machine again via the duct 25. And both air is blade 11
At this time, heat is transferred from the high-temperature drying circulating air 26 to the low-temperature cooling air 27 via the blades 11, and the circulating air 26 is cooled, the water contained therein condenses, becomes water droplets, and is drained from the drain port 28, and the drying circulating air 25 is dehumidified. The dehumidified drying circulation air 26 passes through a ventilation path consisting of an impeller 19, a casing 21, and a partition plate 22, passes through a circulation duct 22, passes through a heater 24, is heated here, and returns to the drum 17. Do this. On the other hand, cooling air 27
is sucked in from outside the machine, enters the impeller 19, cools the drying circulating air 26, and then passes through the exhaust duct 25.
More air is exhausted outside the aircraft.
特に本実施例においては、第６図のように、仕
切板２２の内周部には、フエルト等の可撓性を有
する揺動体２９が設けられており、揺動体２９の
内周部には前記シール材１５と摺動する摺動部３
０が設けられている。 Particularly in this embodiment, as shown in FIG. Sliding portion 3 that slides on the sealing material 15
0 is set.
上記構成では、熱交換型送風機が回転した場
合、前記シール材１５は遠心力および風力により
摺動部３０を挾むように摺動しシールすることに
なるが、循環空気２６側と、冷却空気２７側の負
荷が異なり、第８図のようにPa＞Pbとなつた場
合、シール材１５の摺動部３０のＡ部との摺動抵
抗がＢ部とのそれより大きくなるが、前記揺動体
２９が存在するため、第７図のように摺動部３０
は冷却空気２７側に摺動抵抗差（押圧差）および
圧力差により揺動し、摺動抵抗が均一になつた位
置でシール材１５と摺動部３０が摺動することに
なる。即ち、摺動部３０は常時シール材１５の断
面略Ｖ字型の中央に位置し摺動することになる。 In the above configuration, when the heat exchange type blower rotates, the sealing material 15 slides between and seals the sliding part 30 due to centrifugal force and wind force, but the sealing material 15 is sealed between the circulating air 26 side and the cooling air 27 side. If the loads are different and Pa>Pb as shown in FIG. Because of the presence of the sliding part 30 as shown in FIG.
swings toward the cooling air 27 side due to the sliding resistance difference (pressure difference) and pressure difference, and the sealing material 15 and the sliding portion 30 slide at a position where the sliding resistance becomes uniform. That is, the sliding portion 30 is always located at the center of the substantially V-shaped cross section of the sealing material 15 and slides thereon.
従つて、シール材１５と摺動部３０の摺動抵抗
は、Ａ部、Ｂ部で均一となり、従来の不均一時に
比較し小さくなり、回転トルクの軽減をはかるこ
とができ、シール材１５の耐久性が向上するとい
う効果がある。また、ブレード１１の両側の負荷
が変動しても常に摺動部３０とシール材１５の摺
動抵抗は均一であるため、ブレード１１両面の溝
部分を流れる２種類の空気流は混流することな
く、熱交換効率の向上がはかれるという効果があ
る。 Therefore, the sliding resistance between the sealing material 15 and the sliding part 30 becomes uniform in the A part and the B part, and is smaller than that in the conventional non-uniform case, and the rotational torque can be reduced, and the sliding resistance of the sealing material 15 is This has the effect of improving durability. In addition, even if the load on both sides of the blade 11 changes, the sliding resistance between the sliding part 30 and the sealing material 15 is always uniform, so the two types of airflow flowing through the grooves on both sides of the blade 11 do not mix. This has the effect of improving heat exchange efficiency.
なお上記実施例では、揺動体２９はフエルト等
の可撓体とした例を示したが、リンク機構体であ
つてもよく、要は、摺動部３０が前後方向に揺動
すればよい。 In the above embodiment, the rocking body 29 is made of a flexible body such as felt, but it may also be a link mechanism, as long as the sliding part 30 can swing in the front-rear direction.
発明の効果
上記実施例の説明からあきらかなように、本発
明の熱交換型送風機は、略リング状で断面略Ｖ字
型の可撓性を有するシール材との摺動部を前後方
向に揺動自在としたことにより、常時摺動部がシ
ール材の断面略Ｖ字型の中央に位置することにな
り、回転トルクの軽減と耐久性の向上および熱交
換効率の向上をはかることができるものである。Effects of the Invention As is clear from the description of the above embodiments, the heat exchange type blower of the present invention has a substantially ring-shaped and substantially V-shaped cross-section and swings the sliding part with the flexible sealing material in the front and back direction. By making it freely movable, the sliding part is always located at the center of the approximately V-shaped cross section of the sealing material, which reduces rotational torque, improves durability, and improves heat exchange efficiency. It is.
第１図は従来の熱交換型送風機のインペラを示
す斜視図、第２図は同インペラをケーシングに組
込んだ縦断面図、第３図は同シール部を示す拡大
断面図、第４図は本発明の一実施例を示す熱交換
型送風機のインペラを示す斜視図、第５図は同熱
交換型送風機を用いた除湿式衣類乾燥機の縦断面
図、第６図は同熱交換型送風機の要部断面図、第
７図は同シール部の拡大断面図、第８図は同吐出
圧を示すＰ−Ｑ曲線特性図である。
１１…ブレード、１４…外周板、２２…仕切
材、１５…シール材、２９…揺動体、３０…摺動
部。
Fig. 1 is a perspective view showing the impeller of a conventional heat exchange type blower, Fig. 2 is a vertical cross-sectional view of the impeller assembled into a casing, Fig. 3 is an enlarged sectional view showing the seal part, and Fig. 4 is a perspective view showing the impeller of a conventional heat exchange type blower. A perspective view showing an impeller of a heat exchange type blower showing an embodiment of the present invention, FIG. 5 is a vertical sectional view of a dehumidifying clothes dryer using the same heat exchange type blower, and FIG. 6 is a perspective view of the same heat exchange type blower. 7 is an enlarged sectional view of the seal portion, and FIG. 8 is a P-Q curve characteristic diagram showing the discharge pressure. DESCRIPTION OF SYMBOLS 11... Blade, 14... Outer peripheral plate, 22... Partition material, 15... Seal material, 29... Rocking body, 30... Sliding part.
Claims (1)
形状薄板からなるブレードの外周部を支持する外
周板と、前記外周板の外周部に設けた略リング状
で断面略Ｖ字型の可撓性を有するシール材と、前
記外周板の外周方向に配しブレード両面の溝部分
を流れる２種類の空気流を分離する仕切板を備
え、前記仕切板はシール材との摺動部を前記シー
ル材の断面略Ｖ字型の中央に位置させ、前記摺動
部は前後方向に揺動自在とした熱交換型送風機。1. An outer circumferential plate that supports the outer circumference of the blade, which is made of a corrugated thin plate whose groove portion is located radially from the central axis of rotation, and a flexible plate that is approximately ring-shaped and approximately V-shaped in cross section, provided on the outer circumference of the outer circumferential plate. and a partition plate disposed in the outer circumferential direction of the outer circumferential plate to separate two types of air flows flowing through the groove portions on both sides of the blade, and the partition plate has a sliding part with the seal material. The heat exchange type blower is located at the center of a substantially V-shaped cross section, and the sliding part is swingable in the front and rear directions.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9503884A JPS60238693A (en) | 1984-05-11 | 1984-05-11 | Heat exchange type blower |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9503884A JPS60238693A (en) | 1984-05-11 | 1984-05-11 | Heat exchange type blower |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60238693A JPS60238693A (en) | 1985-11-27 |
| JPH05637B2 true JPH05637B2 (en) | 1993-01-06 |
Family
ID=14126903
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP9503884A Granted JPS60238693A (en) | 1984-05-11 | 1984-05-11 | Heat exchange type blower |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60238693A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8986544B2 (en) | 2009-10-21 | 2015-03-24 | Marmon Water (Singapore) Pte. Ltd. | Vented filter cartridge for water treatment device |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102006029960A1 (en) * | 2006-06-29 | 2008-01-03 | BSH Bosch und Siemens Hausgeräte GmbH | Dryer with reduced noise, suitable blower and impeller and method for producing the impeller |
| EP2113595B1 (en) * | 2008-04-30 | 2011-11-16 | LG Electronics Inc. | Laundry machine |
-
1984
- 1984-05-11 JP JP9503884A patent/JPS60238693A/en active Granted
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8986544B2 (en) | 2009-10-21 | 2015-03-24 | Marmon Water (Singapore) Pte. Ltd. | Vented filter cartridge for water treatment device |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS60238693A (en) | 1985-11-27 |
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