JPH0321811B2 - - Google Patents
Info
- Publication number
- JPH0321811B2 JPH0321811B2 JP57102459A JP10245982A JPH0321811B2 JP H0321811 B2 JPH0321811 B2 JP H0321811B2 JP 57102459 A JP57102459 A JP 57102459A JP 10245982 A JP10245982 A JP 10245982A JP H0321811 B2 JPH0321811 B2 JP H0321811B2
- Authority
- JP
- Japan
- Prior art keywords
- impeller
- heat exchanger
- indoor heat
- refrigerant pipe
- noise
- 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
- 239000003507 refrigerant Substances 0.000 claims description 16
- 238000000926 separation method Methods 0.000 claims description 7
- 230000002159 abnormal effect Effects 0.000 description 7
- 238000002474 experimental method Methods 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 238000007664 blowing Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 230000005856 abnormality Effects 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000030279 gene silencing Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
- F24F1/0025—Cross-flow or tangential fans
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
- F24F1/0057—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in or on a wall
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
- F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
- F24F13/24—Means for preventing or suppressing noise
Description
【発明の詳細な説明】
〔発明の分野〕
本発明は、空気調和機における横流フアンを使
用する室内ユニツトに係り、特に、この室内ユニ
ツトにおける送風消音装置に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of the Invention] The present invention relates to an indoor unit using a cross-flow fan in an air conditioner, and more particularly to an air silencing device for this indoor unit.
最近の空気調和機の室内ユニツトは、室内の設
置面積を小さくする関係上、ケーシングの薄型化
を図つているけれども、このケーシングの薄型化
に伴い、このケーシング内に組込まれる横流フア
ンによる運転時の騒音が、室内での静粛な運転
上、大きな問題になる。
Recent indoor units of air conditioners are designed to have thinner casings in order to reduce the indoor installation area. Noise is a big problem for quiet operation indoors.
第１図は、従来の空気調和機の室内ユニツトで
あつて、この室内ユニツトは、吹出口a1を備えた
ケーシングａの吸込口a2に、例えば、蒸発器によ
る室内熱交換器ｂを設け、この室内熱交換器ｂの
内がわに位置する上記ケーシングａに送風機によ
る羽根車Ｃを設け、この羽根車Ｃの吹出通路ｄの
上記ケーシングａの流路壁a3に、第２図に拡大し
て示されるような、騒音を解消するための段落部
ｅを形成したものである（実開昭55−159931号）。 FIG. 1 shows a conventional air conditioner indoor unit, in which an indoor heat exchanger b using an evaporator, for example, is installed at a suction port a2 of a casing a, which is equipped with a blowout port a1 . , an impeller C by a blower is installed in the casing a located inside the indoor heat exchanger b, and a flow passage wall a 3 of the casing a in the blow-off passage d of the impeller C is shown in FIG. As shown in the enlarged view, a stepped portion e is formed to eliminate noise (Utility Model Application No. 55-159931).
従つて、上述した室内ユニツトは空気調和時、
上記送風機の羽根車Ｃを駆動することにより、室
内の空気を吸込口a2から流入し、これを上記室内
熱交換器ｂで冷風に熱交換した後、上記吹出通路
ｄから吹出口a1へ騒音を発しないようにして涼風
を送風するようになつている。 Therefore, when the indoor unit described above is used for air conditioning,
By driving the impeller C of the blower, indoor air flows in from the suction port a2 , heat exchanges this into cold air in the indoor heat exchanger b, and then flows from the blowout passage d to the blowout port a1. It is designed to blow cool air without making noise.
しかしながら、上述した室内ユニツトは、送風
機の羽根車Ｃから送出される冷風を上記吹出流路
ｄの路上で発生する騒音を消音し得るようにした
ものであるが、吸込口a2から室内熱交換器ｂを通
してケーシングａ内に流入する流体が狭い間隙の
ある吸込流路を通過する際に発生する風切り騒音
や翼ピツチ音による異常音を解消することは困難
である。
However, although the above-mentioned indoor unit is designed to muffle the noise generated on the road in the blowout flow path d by the cold air sent out from the impeller C of the blower, it is possible to muffle the noise generated on the road in the blowout flow path d . It is difficult to eliminate abnormal noise caused by wind noise or blade pitch noise that occurs when fluid flowing into casing a through container b passes through a suction channel with a narrow gap.
又一方、前述したように、室内ユニツトは、室
内の設置面積を小さくする関係上、ケーシングａ
の薄型化に伴い、上記吸込流路がさらに狭く形成
されるため、吸込流体による風切り騒音や翼ピツ
チ音の発生が大きくなり、薄型化に伴う運転時の
消音送風が要望されている。 On the other hand, as mentioned above, in order to reduce the indoor installation area, the indoor unit has a casing a.
As the thickness of the pump becomes thinner, the suction flow path becomes narrower, which increases wind noise and blade pitch noise caused by the suction fluid.Therefore, there is a demand for noiseless air blowing during operation as the thickness of the pump becomes thinner.
しかしながら、横流フアンの羽根車を使用する
室内ユニツトは、ケーシングの薄型化を推進した
場合、室内熱交換器と羽根車との離間距離を大幅
に短縮することを余儀なくされるため、この離間
距離を小さくすると、羽根車の翼ピツチ音と呼ば
れる“高周波振動”による騒音が発生し、ケーシ
ングの薄型化を図ることが困難とされている。 However, in indoor units that use cross-flow fan impellers, if the casing is made thinner, the distance between the indoor heat exchanger and the impeller must be significantly shortened. If it is made smaller, noise due to "high frequency vibration" called impeller blade pitch noise will be generated, making it difficult to make the casing thinner.
本発明は、上述した事情に鑑みてなされたもの
であつて、羽根車の翼ピツチ音による高周波振動
を解消すると共に、併せて、ケーシングの薄型化
を図り、静粛な送風をすることを目的とする空気
調和機の室内ユニツトを提供するものである。
The present invention has been made in view of the above-mentioned circumstances, and aims to eliminate high-frequency vibrations caused by impeller blade pitch noise, and at the same time, to reduce the thickness of the casing and provide quiet air blowing. The present invention provides an indoor unit for an air conditioner.
本発明は、吹出口を備えたケーシングの吸込口
に近接して室内熱交換器を設け、この室内熱交換
器の下位にドレン皿を配設し、上記室内熱交換器
の内がわに位置する横流フアンの羽根車を設けた
室内ユニツトにおいて、上記室内熱交換器の最下
位の冷媒管と上記羽根車との離間距離をＨとし、
上記冷媒管と上記ドレン皿のノーズとの離間距離
をＣとし、上記離間距離Ｈを上記羽根車の直径Ｄ
の約15％程度としたとき、上記離間距離Ｃを約５
mm程度に構成したものである。
The present invention provides an indoor heat exchanger close to a suction port of a casing equipped with an air outlet, and a drain plate is disposed below this indoor heat exchanger, and is located inside the indoor heat exchanger. In an indoor unit equipped with a cross-flow fan impeller, the distance between the lowest refrigerant pipe of the indoor heat exchanger and the impeller is H,
The separation distance between the refrigerant pipe and the nose of the drain pan is C, and the separation distance H is the diameter D of the impeller.
When the above distance C is about 15% of the
It is designed to have a diameter of about mm.
以下、本発明を図示の一実施例について説明す
る。
Hereinafter, the present invention will be described with reference to an illustrated embodiment.
第３図及び第４図において、符号１は、室内ユ
ニツトにおける箱形のケーシングであつて、この
ケーシング１の正面には室内空気を流入する吸込
口２が形成されており、この吸込口２の内がわに
近接して位置するケーシング１内には、例えば、
蒸発器による室内熱交換器３が設置されている。
又、この室内熱交換器３の下位には、ドレン皿４
が間隙５を存して設けられており、このドレン皿
及び上記室内熱交換器３の内がわに位置する上記
ケーシング１には横流フアンの羽根車６が設けら
れている。さらに、この羽根車６の吹出流路７に
は冷風の吹出口８が形成されており、この吹出口
８は冷風を下向きにして室内へ送風するようにな
つている。 In FIGS. 3 and 4, reference numeral 1 denotes a box-shaped casing in the indoor unit, and an inlet 2 through which room air flows is formed in the front of the casing 1. In the casing 1 located close to the inner side, for example,
An indoor heat exchanger 3 using an evaporator is installed.
Further, a drain plate 4 is provided below the indoor heat exchanger 3.
is provided with a gap 5 in between, and an impeller 6 of a cross-flow fan is provided on the drain plate and the casing 1 located inside the indoor heat exchanger 3. Further, a cold air outlet 8 is formed in the outlet passage 7 of the impeller 6, and the outlet 8 is configured to blow the cold air downward into the room.
一方、上記室内熱交換器３の最下位の冷媒管３
ａ上記羽根車６の外周とには離間距離Ｈの間隙が
形成されており、上記冷媒管３ａと上記ドレン皿
４のノーズ４ａとには離間距離Ｃの間隙が形成さ
れている。 On the other hand, the lowest refrigerant pipe 3 of the indoor heat exchanger 3
a A gap of a distance H is formed between the outer periphery of the impeller 6, and a gap of C is formed between the refrigerant pipe 3a and the nose 4a of the drain plate 4.
特に、上記離間距離Ｈは、上記羽根車６の直径
（外径）Ｄの約15％としており、他方、上記離間
距離Ｃの間隙は約５mm以内に形成されている。 In particular, the separation distance H is about 15% of the diameter (outer diameter) D of the impeller 6, and the gap C is about 5 mm or less.
即ち、上記室内ユニツトにおける横流フアンの
羽根車６の回転時、上記室内熱交換器３の最下位
の冷媒管３ａの下流側には、第４図の鎖線で示さ
れるように、パイプによる渦流部αが発生する。
この冷媒管３ａが上記横流フアンの羽根車６と接
近しているときには、上記渦流部αの作用によつ
て、上記冷媒管３ａと上記ノーズ４ａとの間隙を
通過した気流が、充分に拡散することなく、上記
羽根車６に吸い込まれるため、羽根車６に対する
吸い込み気流分布に不均一な気流分布を生じ、上
記冷媒管３ａと上記ノーズ４ａの間から吸込まれ
る風速は、この冷媒管３ａよりも上部の気流より
も早い流速となり、この高速度の気流が回転して
いる上記羽根車６の各羽根を通過するごとに、い
わゆる、翼ピツチ音と呼ばれる異常音を発生す
る。この異常音は、第５図のグラフの点線で示さ
れるような曲線Ａを描くことを実験の結果確認し
た。 That is, when the impeller 6 of the cross-flow fan in the indoor unit rotates, a vortex section formed by a pipe is formed on the downstream side of the lowest refrigerant pipe 3a of the indoor heat exchanger 3, as shown by the chain line in FIG. α occurs.
When this refrigerant pipe 3a is close to the impeller 6 of the cross-flow fan, the airflow that has passed through the gap between the refrigerant pipe 3a and the nose 4a is sufficiently diffused by the action of the vortex section α. Since the air is sucked into the impeller 6 without any movement, a non-uniform airflow distribution occurs in the suction airflow distribution with respect to the impeller 6, and the wind speed sucked from between the refrigerant pipe 3a and the nose 4a is The flow velocity of the airflow is higher than that of the upper airflow, and each time this high-velocity airflow passes through each blade of the rotating impeller 6, an abnormal sound called a so-called blade pitch sound is generated. As a result of experiments, it was confirmed that this abnormal sound draws a curve A as shown by the dotted line in the graph of FIG.
この曲線Ａによる異常音（翼ピツチ音）は、
横流フアンの羽根枚数×フアン回転数
による高周波振動であつて、
羽根直径……90mm、羽根枚数……24枚、
フアン回転数……1300r.p.mのとき、
翼ピツチ音は530Hzとなり、このときの騒音レベ
ルは約40dBとなる。 The abnormal sound (blade pitch noise) caused by this curve A is a high-frequency vibration caused by the number of blades of the crossflow fan x fan rotation speed, and the blade diameter is 90 mm, the number of blades is 24, and the fan rotation speed is 1300 r.pm. At this time, the blade pitch sound is 530Hz, and the noise level at this time is approximately 40dB.
そこで本発明は、異常音ピークの大きさと、こ
の異常音発生因子となる羽根車６の直径Ｄ、冷媒
管３ａとノーズ４ａの離間距離Ｃ及び冷媒管３ａ
と羽根車６との離間距離Ｈとの関係を実験によつ
て、その結果を得ることができた。 Therefore, the present invention aims to determine the magnitude of the abnormal sound peak, the diameter D of the impeller 6 which is a factor in generating this abnormal sound, the separation distance C between the refrigerant pipe 3a and the nose 4a, and the refrigerant pipe 3a.
The relationship between the distance H and the impeller 6 was determined by experiment.
即ち、本発明によれば、横流フアンの羽根車６
の外径Ｄを75mm，90mm，100mmのいずれの場合も、
Ｈ／Ｄ≦0.15
の範囲内では、
Ｃ≦５mm
となる。 That is, according to the present invention, the impeller 6 of the crossflow fan
Regardless of whether the outer diameter D is 75mm, 90mm, or 100mm, within the range of H/D≦0.15, C≦5mm.
これは、Ｃ≦５mmとすることにより、吸い込ま
れる流体は、冷媒管３ａとノーズ４ａの直前で急
激に縮小されて、これが上記間隙Ｃを通つた後、
広がつて減圧されるから、流速が低下し、翼ピツ
チ音による異常音の発生はなくなる。 This is because by setting C≦5mm, the sucked fluid is rapidly reduced just before the refrigerant pipe 3a and the nose 4a, and after passing through the gap C,
Since it spreads out and is depressurized, the flow velocity decreases and abnormal noises due to blade pitching noises are no longer generated.
即ち、本発明による実験の結果によれば、
(1) 羽根車の直径Ｄ＝75mm
羽根車の羽根枚数……27枚
回転数……1500r.p.m
間隙Ｃ＝３，４，５，６，８，10mmとしたと
きの騒音レベルdBは、第６図に示される各曲
線となる。 That is, according to the results of experiments according to the present invention, (1) Impeller diameter D = 75 mm Number of impeller blades...27 Number of rotations...1500 r.pm Gap C = 3, 4, 5, 6, 8 , 10mm, the noise level dB becomes the curves shown in Figure 6.
従つて、この第６図のグラフからも明らかな
ように騒音レベルdBはＣ＝３，４，５mm程度
が望ましい。この場合、第５図の曲線Ｂで示す
曲線となる。 Therefore, as is clear from the graph of FIG. 6, it is desirable that the noise level dB is about C=3, 4, or 5 mm. In this case, the curve becomes a curve shown as curve B in FIG.
(2) 羽根車の直径Ｄ＝90mm
羽根車の羽根枚数……24枚
回転数……1300r.p.m
間隙Ｃ＝３，４，５，６，８，10mm
としたときの騒音レベルdBは、第７図に示さ
れる各曲線となる。(2) Impeller diameter D = 90mm Number of impeller blades...24 Number of rotations...1300r.pm The noise level dB when gap C=3, 4, 5, 6, 8, 10mm is The curves are shown in Figure 7.
従つて、この第７図のグラフからも明らかな
ように、騒音レベルdBは、Ｃ＝３，４，５mm
程度が望ましい。 Therefore, as is clear from the graph in Figure 7, the noise level dB is C = 3, 4, 5 mm.
degree is desirable.
(3) 羽根車の直径Ｄ＝100mm
羽根車の羽根枚数……30枚
回転数……1200r.p.m
間隙Ｃ＝３，４，５，６，８，10mm
としたときの騒音レベルdBは、第８図に示さ
れる各曲線となる。(3) Impeller diameter D = 100mm Number of impeller blades...30 Number of rotations...1200r.pm The noise level dB when the gap C=3, 4, 5, 6, 8, 10mm is The curves shown in Figure 8 are obtained.
従つて、この第８図のグラフからも明かなよ
うに、騒音レベルdBは、Ｃ＝３，４，５mm程
度が望ましい。 Therefore, as is clear from the graph of FIG. 8, it is desirable that the noise level dB is about C=3, 4, or 5 mm.
以上述べたように本発明によれば、室内熱交換
器３の最下位の冷媒管３ａと羽根車６との離間距
離をＨとし、上記冷媒管３ａとドレン皿４のノー
ズ４ａとの離間距離をＣとし、上記離間距離Ｈを
上記羽根車の直径Ｄの約15％程度としたとき、上
記離間距離Ｃを約５mm程度にしてあるので、ケー
シング１を薄型化しても、翼ピツチ音による異常
音の発生を解消することができると共に、静粛な
空気調和機を施すことができる。
As described above, according to the present invention, the distance between the lowest refrigerant pipe 3a of the indoor heat exchanger 3 and the impeller 6 is H, and the distance between the refrigerant pipe 3a and the nose 4a of the drain tray 4 is H. is C, and the above-mentioned separation distance H is about 15% of the impeller diameter D. Since the above-mentioned separation distance C is about 5 mm, even if the casing 1 is made thinner, there will be no abnormality due to blade pitch noise. The generation of noise can be eliminated, and a quiet air conditioner can be provided.
第１図は、従来の空気調和機の室内ユニツトの
断面図、第２図は、第１図中の鎖円Ａ部の拡大
図、第３図は、本発明による空気調和機の室内ユ
ニツトの断面図、第４図は、本発明の作用を説明
するための図、第５図乃至第８図は、騒音レベル
の関係を示すグラフである。
１……ケーシング、２……吸込口、３……室内
熱交換器、３ａ……冷媒管、４……ドレン皿、４
ａ……ノーズ、６……羽根車、８……吹出口。
Fig. 1 is a sectional view of a conventional indoor unit of an air conditioner, Fig. 2 is an enlarged view of the chain circle A section in Fig. 1, and Fig. 3 is a cross-sectional view of an indoor unit of an air conditioner according to the present invention. The sectional view and FIG. 4 are diagrams for explaining the action of the present invention, and FIGS. 5 to 8 are graphs showing the relationship between noise levels. 1... Casing, 2... Suction port, 3... Indoor heat exchanger, 3a... Refrigerant pipe, 4... Drain plate, 4
a... Nose, 6... Impeller, 8... Air outlet.
Claims (1)
て室内熱交換器を設け、この室内熱交換器の下位
にドレン皿を配設し、上記室内熱交換器の内がわ
に位置する横流フアンの羽根車を設けた室内ユニ
ツトにおいて、上記室内熱交換器の最下位の冷媒
管と上記羽根車との離間距離をＨとし、上記冷媒
管と上記ドレン皿のノーズとの離間距離をＣと
し、上記離間距離Ｈを上記羽根車の直径Ｄの約15
％程度としたとき、上記離間距離Ｃを約５mm程度
にしたことを特徴とする空気調和機の室内ユニツ
ト。1. An indoor heat exchanger is provided close to the suction port of the casing equipped with an air outlet, a drain plate is provided below the indoor heat exchanger, and a cross-flow fan is located inside the indoor heat exchanger. In an indoor unit equipped with an impeller, the distance between the lowest refrigerant pipe of the indoor heat exchanger and the impeller is H, the distance between the refrigerant pipe and the nose of the drain pan is C, The above distance H is approximately 15 times the diameter D of the impeller.
%, the above-mentioned separation distance C is approximately 5 mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57102459A JPS58219337A (en) | 1982-06-15 | 1982-06-15 | Indoor unit of air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57102459A JPS58219337A (en) | 1982-06-15 | 1982-06-15 | Indoor unit of air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS58219337A JPS58219337A (en) | 1983-12-20 |
| JPH0321811B2 true JPH0321811B2 (en) | 1991-03-25 |
Family
ID=14328044
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP57102459A Granted JPS58219337A (en) | 1982-06-15 | 1982-06-15 | Indoor unit of air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS58219337A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2637662B2 (en) * | 1992-02-25 | 1997-08-06 | ローム株式会社 | Method of manufacturing chip-type composite electronic component and method of manufacturing chip-type network resistor |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103673084B (en) * | 2012-09-24 | 2016-05-04 | 珠海格力电器股份有限公司 | Air conditioner room unit, there is the control method of its air-conditioner and indoor set |
| JP6843721B2 (en) * | 2017-09-27 | 2021-03-17 | ダイキン工業株式会社 | Air conditioner |
| JP2022136087A (en) * | 2019-10-30 | 2022-09-15 | ダイキン工業株式会社 | air conditioner |
-
1982
- 1982-06-15 JP JP57102459A patent/JPS58219337A/en active Granted
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2637662B2 (en) * | 1992-02-25 | 1997-08-06 | ローム株式会社 | Method of manufacturing chip-type composite electronic component and method of manufacturing chip-type network resistor |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS58219337A (en) | 1983-12-20 |
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