JP3484854B2 - Once-through fan - Google Patents
Once-through fanInfo
- Publication number
- JP3484854B2 JP3484854B2 JP00644796A JP644796A JP3484854B2 JP 3484854 B2 JP3484854 B2 JP 3484854B2 JP 00644796 A JP00644796 A JP 00644796A JP 644796 A JP644796 A JP 644796A JP 3484854 B2 JP3484854 B2 JP 3484854B2
- Authority
- JP
- Japan
- Prior art keywords
- flow fan
- present
- cross flow
- blade
- once
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
- F04D17/02—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal
- F04D17/04—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps having non-centrifugal stages, e.g. centripetal of transverse-flow type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/26—Rotors specially for elastic fluids
- F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
- F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
- F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
- F04D29/283—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis rotors of the squirrel-cage type
Description
【０００１】[0001]
【発明の属する技術分野】この発明は、貫流送風機に係
り、羽根車の回転音で特に低周波数帯の騒音発生を抑え
るようにしたものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a cross-flow fan, and is intended to suppress the generation of noise particularly in a low frequency band due to the rotating sound of an impeller.
【０００２】[0002]
【従来の技術】従来の空気調和機室内機５は、図７に示
すようにケーシング６の前面下側部分に空気吹き出しノ
ズル７を設け、その上方に空気吸い込み口８を設け、更
にその後側に熱交換器９を配置して構成されていて、前
記ケーシング６と熱交換器９の間に配置された貫流送風
羽根車４によって、空気吸い込み口８から導入された空
気を、熱交換器９を通過する際に熱交換させ、冷風もし
くは温風とし、空気吹き出しノズル７から室内に吹き出
すようにしている。2. Description of the Related Art As shown in FIG. 7, a conventional air conditioner indoor unit 5 is provided with an air blowing nozzle 7 in a lower portion of a front surface of a casing 6, an air suction port 8 above the air blowing nozzle 7, and a rear side thereof. The heat exchanger 9 is arranged so that the air introduced from the air suction port 8 is transferred to the heat exchanger 9 by the cross flow fan impeller 4 arranged between the casing 6 and the heat exchanger 9. When passing, heat is exchanged to make cold air or warm air, and the air is blown out from the air blowing nozzle 7.
【０００３】前記貫流送風羽根車は、図８に示すよう
に、回転軸に対して直角なる複数の仕切板３と、前記仕
切板の間に複数の羽根１を羽根取り付け間隔を周期性を
もたせて備えたものである。 ここで羽根車４が回転す
るときに発生する音、即ち、羽根の枚数に関係したファ
ン回転音（以下、ＮＺ音と言う）を低減するために、例
えば、特開昭６０−１７２９６号公報に示されているよ
うに、羽根１は取り付け間隔を周期性を持たせず乱数的
に配列して構成されている。As shown in FIG. 8, the cross flow fan impeller is provided with a plurality of partition plates 3 perpendicular to the rotation axis, and a plurality of blades 1 between the partition plates with a periodical blade mounting interval. It is a thing. Here, in order to reduce a sound generated when the impeller 4 rotates, that is, a fan rotating sound (hereinafter, referred to as NZ sound) related to the number of blades, for example, Japanese Patent Laid-Open No. 60-17296. As shown in the figure, the blades 1 are arranged by randomly mounting the mounting intervals without periodicity.
【０００４】[0004]
【発明が解決しようとする課題】従来の貫流送風羽根車
は上記のように構成されており、図９に示す羽根取り付
け間隔が周期性を持たせた構成の羽根車の騒音値周波数
分析の結果を、図１０の特開昭６０−１７２９６号公報
に示されたような、羽根取り付け間隔が周期性を持たな
い構成の羽根車の騒音値周波数分析の結果を示す。特開
昭６０−１７２９６号公報のように羽根を取り付けた場
合、ＮＺ音を低減することは可能であるが、図１０に示
されるように６００Ｈｚ以下の低周波数の騒音が新たに
発生してしまう。The conventional through-flow blower impeller is constructed as described above, and the result of the noise value frequency analysis of the impeller of the construction shown in FIG. 10 shows a result of noise value frequency analysis of an impeller having a configuration in which the blade mounting intervals have no periodicity as shown in Japanese Patent Laid-Open No. 60-17296. When the blade is attached as in Japanese Patent Laid-Open No. 60-17296, it is possible to reduce the NZ noise, but as shown in FIG. 10, low frequency noise of 600 Hz or less is newly generated. .
【０００５】図１０は以下の数２式により羽根を乱数的
に配列した場合の周波数分析のシミュレーション結果で
ある。FIG. 10 shows a simulation result of frequency analysis when the blades are arranged in a random number by the following equation (2).
【０００６】[0006]
【数２】 [Equation 2]
【０００７】これは、スタビライザー１０の付近を貫流
送風羽根車４の羽根１が通過するとき、羽根１で生じる
圧力変動から発する騒音は、歪み係数δが大きくなれば
なる程、羽根１間での相関は小さくなりＮＺ音は減少す
る、一方、単独で発生するファン回転音（以下、Ｎ音と
言う）は低周波数帯に於いて目立つように発生してく
る。This is because when the blades 1 of the once-through fan impeller 4 pass near the stabilizer 10, the noise generated from the pressure fluctuations generated in the blades 1 is increased between the blades 1 as the distortion coefficient δ increases. The correlation becomes smaller and the NZ sound is reduced, while the fan rotation sound (hereinafter referred to as N sound) generated independently is conspicuously generated in the low frequency band.
【０００８】そこで、この発明は、ＮＺ音を減少させ、
更に低周波数帯（６００Ｈｚ以下）のＮ音の騒音発生も
同時に抑えるようにした貫流送風羽根車を得ることを目
的とする。Therefore, the present invention reduces the NZ sound,
Further, it is an object of the present invention to obtain a cross flow fan impeller in which noise generation of N sound in a low frequency band (600 Hz or less) is also suppressed.
【０００９】[0009]
【課題を解決するための手段】この発明の請求項１にか
かる貫流送風羽根車は、羽根の取り付け位置を基準羽根
をスタートに以下に示す式に従い、羽根の取り付け位置
を定める配置角度θｋは、基準角度に配置されている羽
根を０とした場合の羽根番号をｋとすると、配置角変動
量α及びサイクリック次数βにより、下記の数３に示す
ように定義したものでである。According to a first aspect of the present invention, there is provided a cross flow fan impeller in which an installation angle θk for determining a mounting position of the blade is determined according to the following equation with a reference blade as a mounting position of the blade. When the blade number arranged when the blade arranged at the reference angle is 0 is k, the blade angle is defined by the arrangement angle variation amount α and the cyclic order β as shown in the following Expression 3.
【００１０】[0010]
【数３】 [Equation 3]
【００１１】この発明の請求項２にかかる貫流送風羽根
車は、サイクリック次数βを２以上の自然数とするもの
である。According to the second aspect of the present invention, the once-through blower impeller has a cyclic order β of a natural number of 2 or more.
【００１２】この発明の請求項３にかかる貫流送風羽根
車は、サイクリック次数βを２以上の自然数で、かつ偶
数とするものである。According to the third aspect of the present invention, the through-flow fan impeller has a cyclic order β that is a natural number of 2 or more and that is an even number.
【００１３】この発明の請求項４にかかる貫流送風羽根
車は、配置角変動量αは、０＜α＜１の範囲の有理数と
するものである。In the once-through blower impeller according to the fourth aspect of the present invention, the arrangement angle variation amount α is a rational number in the range of 0 <α <1.
【００１４】この発明の請求項５にかかる貫流送風羽根
車は、スキュー角を設けて形成したものである。The cross flow fan impeller according to claim 5 of the present invention is formed with a skew angle.
【００１５】この発明の請求項６にかかる貫流送風羽根
車は、スキュー角を設け、かつサイクリック次数βを２
以上の自然数とするものである。According to a sixth aspect of the present invention, there is provided a cross flow fan impeller having a skew angle and a cyclic order β of 2
The above is a natural number.
【００１６】この発明の請求項７にかかる貫流送風羽根
車は、スキュー角を設け、かつサイクリック次数βを２
以上の自然数かつ偶数とするものである。According to a seventh aspect of the present invention, there is provided a cross flow fan impeller having a skew angle and a cyclic order β of 2
The above is a natural number and an even number.
【００１７】この発明の請求項８にかかる貫流送風羽根
車は、スキュー角を設け、かつ配置角変動量αは、０＜
α＜１の範囲の有理数とするものである。According to the eighth aspect of the present invention, there is provided a cross flow fan impeller having a skew angle, and the arrangement angle variation amount α is 0 <
It is a rational number in the range of α <1.
【００１８】[0018]
実施の形態１．図１にこの発明の実施の形態１を示す。
図１において、１は羽根、２は基準羽根、３は仕切板、
θは羽根取り付け位置を定める配置角度、４はこれら羽
根１、基準羽根２及び仕切板３に羽根取り付け位置を定
める配置角度θにより形成された羽根車である。羽根取
り付けは位置角度の式を数４に示す、Embodiment 1. FIG. 1 shows a first embodiment of the present invention.
In FIG. 1, 1 is a blade, 2 is a reference blade, 3 is a partition plate,
θ is an arrangement angle that determines the blade attachment position, and 4 is an impeller formed by the arrangement angle θ that determines the blade attachment position on the blade 1, the reference blade 2, and the partition plate 3. The blade mounting shows the formula of the position angle in Equation 4,
【００１９】[0019]
【数４】 [Equation 4]
【００２０】により定義され、配置角変動量α＝０．
２、サイクリック次数β＝２、均等間隔での翼間角度ｄ
θ＝２π／３５、均等間隔に配置された場合の配置角度
θｋ０＝２π×ｋ／３５、とした場合の羽根取り付け位
置を定める配置角度である。And the arrangement angle variation amount α = 0.
2, cyclic order β = 2, blade angle d at equal intervals
This is an arrangement angle that determines the blade mounting position when θ = 2π / 35 and the arrangement angle θk0 = 2π × k / 35 when the blades are arranged at equal intervals.
【００２１】図２に、この発明の実施の形態１の羽根車
４を組み込んだ空気調和機を示す。５は空気調和機の室
内機、６はケーシング、７は空気吹き出し口、８は空気
吸い込み口、９は熱交換器、１０はスタビライザーであ
る。図３には、この発明の実施の形態１の羽根１位置を
サインカーブに対比させた場合の図を示すものである。FIG. 2 shows an air conditioner incorporating the impeller 4 of Embodiment 1 of the present invention. Reference numeral 5 is an indoor unit of an air conditioner, 6 is a casing, 7 is an air outlet, 8 is an air inlet, 9 is a heat exchanger, and 10 is a stabilizer. FIG. 3 shows a diagram in which the position of the blade 1 according to the first embodiment of the present invention is compared with a sine curve.
【００２２】この発明の実施の形態１に於ける貫流送風
羽根車は、羽根１の取り付け位置をサイクリックに変動
させているため、図４に示すようにＮＺ音に変調がかか
りピークレベルは分散され騒音レベルが下がる一方、単
独で発生するＮ音は相関が残っていることにより、騒音
レベルは抑制される。In the once-through blower impeller according to the first embodiment of the present invention, since the mounting position of the blade 1 is cyclically changed, the NZ sound is modulated and the peak level is dispersed as shown in FIG. While the noise level decreases, the noise level is suppressed because the N sound generated independently remains in correlation.
【００２３】実施の形態２．この発明の実施の形態２の
貫流送風羽根車は、上記実施の形態１において、サイク
リック次数βは２以上の自然数とするものであり、この
結果、変調が大きくかかり、サイクリックの効果を十分
に得ることが出来るものである。Embodiment 2. The cross flow fan impeller according to the second embodiment of the present invention has a cyclic order β that is a natural number of 2 or more in the first embodiment, and as a result, the modulation is large and the cyclic effect is sufficiently effective. Can be obtained.
【００２４】実施の形態３．この発明の実施の形態３の
貫流送風羽根車は、上記実施の形態１において、サイク
リック次数βは２以上の自然数で、かつ偶数とすると、
機械的バランスを同時にとることができるものである。Embodiment 3. According to the once-through blower impeller of the third embodiment of the present invention, when the cyclic order β is a natural number of 2 or more and is an even number in the first embodiment,
Mechanical balance can be achieved at the same time.
【００２５】実施の形態４．この発明の実施の形態４の
貫流送風羽根車は、上記実施の形態１において、配置角
変動量αは０＜α＜１の範囲の有理数とする。これによ
り翼間隔が均等になったり、隣の翼と重なったりしない
ものである。Fourth Embodiment The once-through air blower according to the fourth embodiment of the present invention is the ratio of the arrangement angle variation α in the range of 0 <α <1 in the first embodiment. As a result, the wings are not evenly spaced and do not overlap with the adjacent wings.
【００２６】実施の形態５．この発明の実施の形態５の
貫流送風羽根車においては、図６に示すようにスキュー
角θ′を付けものにおいては、ＮＺ音低減に大きな効果
を与えることが、一般に知られていることだが、これに
上記実施の形態１を付加する。これにより、ＮＺ音低減
に相乗効果が得られる。Embodiment 5. It is generally known that, in the once-through blower impeller of Embodiment 5 of the present invention, the one having a skew angle θ ′ as shown in FIG. 6 has a great effect on reducing the NZ sound. The first embodiment is added to this. Thereby, a synergistic effect can be obtained in reducing the NZ sound.
【００２７】実施の形態６．この発明の実施の形態６の
貫流送風羽根車は、上記実施の形態５において、サイク
リック次数βは２以上の自然数とする。この結果、変調
が大きくかかり、サイクリックの効果を十分に得ること
が出来る。Sixth Embodiment In the once-through blower impeller according to the sixth embodiment of the present invention, the cyclic order β is a natural number of 2 or more in the fifth embodiment. As a result, a large amount of modulation is required, and a sufficient cyclic effect can be obtained.
【００２８】実施の形態７．この発明の実施の形態７の
貫流送風羽根車は、上記実施の形態５において、サイク
リック次数βは２以上の自然数かつ偶数とすると、機械
的バランスを同時にとることができるものである。Embodiment 7. The once-through blower impeller according to the seventh embodiment of the present invention can have mechanical balance at the same time as in the fifth embodiment, if the cyclic order β is a natural number of 2 or more and an even number.
【００２９】実施の形態８．この発明の実施の形態８の
貫流送風羽根車は、上記実施の形態５において、配置角
変動量αは０＜α＜１の範囲の有理数とする。これによ
り翼間隔が均等になったり、隣の翼と重なったりしない
ものである。Embodiment 8. In the once-through blower impeller of Embodiment 8 of the present invention, the arrangement angle variation amount α is a rational number in the range of 0 <α <1 in Embodiment 5 described above. As a result, the wings are not evenly spaced and do not overlap with the adjacent wings.
【００３０】[0030]
【発明の効果】この発明の請求項１にかかる貫流送風羽
根車は、回転軸に対して直角なる複数の仕切板と、前記
仕切板の間に複数の羽根を備え、羽根の取り付け位置が
以下の数１に示す式による間隔に配置する構成としたか
ら、The cross flow fan impeller according to claim 1 of the present invention is provided with a plurality of partition plates perpendicular to the rotation axis and a plurality of blades between the partition plates, and the mounting positions of the blades are as follows. Since it is arranged at intervals according to the formula shown in 1,
【００３１】[0031]
【数５】 [Equation 5]
【００３２】羽根の取り付け位置をサイクリックに変動
させているため、ＮＺ音に変調がかかりピークレベルは
分散され騒音レベルが下がる一方、単独で発生するＮ音
は相関が残っていることにより、騒音レベルは抑制され
る効果を有する。Since the mounting positions of the blades are cyclically changed, the NZ sound is modulated, the peak level is dispersed and the noise level is lowered, while the N sound generated independently remains the noise. The level has the effect of being suppressed.
【００３３】この発明の請求項２にかかる貫流送風羽根
車は、サイクリック次数βを２以上の自然数にする構成
にしたから、サイクリックの効果を十分に得ることが可
能となる効果を有する。Since the once-through type blower impeller according to claim 2 of the present invention has a structure in which the cyclic order β is a natural number of 2 or more, there is an effect that a sufficient cyclic effect can be obtained.
【００３４】この発明の請求項３にかかる貫流送風羽根
車は、サイクリック次数βを２以上の自然数かつ偶数と
する構成にしたから、貫流送風羽根車の機械的バランス
を取ることが可能となる効果を有する。Since the cross flow fan impeller according to claim 3 of the present invention has a structure in which the cyclic order β is a natural number of 2 or more and an even number, the mechanical balance of the cross flow fan can be achieved. Have an effect.
【００３５】この発明の請求項４にかかる貫流送風羽根
車は、α＝０では均等間隔に羽根を取り付けたこととな
り、ＮＺ音を減少させることが不可能となり、又、α＝
１では隣の羽根と重なってしまうが、配置角変動量αを
０＜α＜１とする構成としたから、翼間隔が均等になっ
たり、隣の翼と重なったりしない効果を有する。In the once-through blower impeller according to claim 4 of the present invention, when α = 0, the blades are attached at equal intervals, and it becomes impossible to reduce the NZ noise, and α =
When it is 1, the blade overlaps with the adjacent blade, but since the arrangement angle variation amount α is set to 0 <α <1, it has an effect that the blade intervals are not even and do not overlap with the adjacent blade.
【００３６】この発明の請求項５にかかる貫流送風羽根
車は、スキュー角の付いている貫流送風羽根車に請求項
１の構成を付加する構成としたから、図７に示すように
スキューのみで抑制しきれないピーク音を図８に示すよ
うに、更に抑制することが可能となる効果を有する。The cross flow fan impeller according to claim 5 of the present invention has a structure in which the structure of claim 1 is added to the cross flow fan impeller having a skew angle. Therefore, as shown in FIG. As shown in FIG. 8, the peak sound that cannot be suppressed is further suppressed.
【００３７】この発明の請求項６にかかる貫流送風羽根
車は、スキュー角を設け、かつサイクリック次数βを２
以上の自然数とする構成にしたから、サイクリックの効
果を十分に得ることが可能となる効果を有する。According to a sixth aspect of the present invention, there is provided a cross flow fan impeller having a skew angle and a cyclic order β of 2
Since the above natural number configuration is adopted, it is possible to obtain a sufficient cyclic effect.
【００３８】この発明の請求項７にかかる貫流送風羽根
車は、、スキュー角を設け、かつサイクリック次数βを
２以上の自然数かつ偶数とする構成としたから、貫流送
風羽根車の機械的バランスを取ることが可能となる効果
を有する。Since the cross flow fan impeller according to claim 7 of the present invention has a structure in which the skew angle is provided and the cyclic order β is a natural number of 2 or more and an even number, the mechanical balance of the cross flow fan impeller is Has the effect of being able to take.
【００３９】この発明の請求項８にかかる貫流送風羽根
車は、スキュー角を設け、かつ配置角変動量αは、０＜
α＜１の範囲の有理数とする構成としたから、翼間隔が
均等になり、隣の翼と重なったりしない効果を有する。According to the eighth aspect of the present invention, the cross flow fan impeller has a skew angle, and the arrangement angle variation amount α is 0 <
Since the ratio is a rational number in the range of α <1, it has an effect that the blade intervals are uniform and do not overlap with the adjacent blades.
【図１】 この発明の実施の形態１を示す貫流送風羽根
車の断面図である。FIG. 1 is a cross-sectional view of a cross-flow fan impeller showing a first embodiment of the present invention.
【図２】 この発明の実施の形態１を示す貫流送風羽根
車を組み込んだ空気調和機の断面図である。FIG. 2 is a cross-sectional view of an air conditioner incorporating the once-through blower impeller according to the first embodiment of the present invention.
【図３】 この発明の実施の形態１の羽根位置をサイン
カーブに対比させた説明図。FIG. 3 is an explanatory diagram comparing the blade position of the first embodiment of the present invention with a sine curve.
【図４】 この発明の実施の形態１による貫流送風羽根
車の騒音値周波数分析結果を示す特性図である。FIG. 4 is a characteristic diagram showing a noise value frequency analysis result of the once-through blower impeller according to the first embodiment of the present invention.
【図５】この発明の実施の形態５の貫流送風羽根車のス
キュー角を示す説明図である。FIG. 5 is an explanatory diagram showing a skew angle of a once-through blower impeller according to a fifth embodiment of the present invention.
【図６】この発明の実施の形態５のスキュー角のみでの
貫流送風羽根車の騒音値周波数分析結果を示す特性図で
ある。FIG. 6 is a characteristic diagram showing a result of noise value frequency analysis of a once-through blower impeller with only a skew angle according to the fifth embodiment of the present invention.
【図７】 従来の空気調和機室内機。FIG. 7 is a conventional air conditioner indoor unit.
【図８】 従来の貫流送風羽根車。FIG. 8 is a conventional once-through blower impeller.
【図９】 従来の羽根取り付け間隔が周期性を持つ貫流
送風羽根車の騒音値周波数分析結果を示す特性図であ
る。FIG. 9 is a characteristic diagram showing a noise value frequency analysis result of a conventional once-through air blower having a periodic blade attachment interval.
【図１０】 従来の貫流送風羽根車の騒音値周波数分析
結果を示す特性図である。FIG. 10 is a characteristic diagram showing a result of noise value frequency analysis of a conventional cross-flow fan.
１ 羽根、２ 基準羽根、３ 羽根取り付け位置を定め
る配置角度、４ 仕切板、５ スキュー角、６ ケーシ
ング、７ 空気吹き出しノズル、８ 空気吸い込み口、
９ 熱交換器、１０ スタビライザー、１１ 貫流送風
羽根車1 blade, 2 reference blade, 3 arrangement angle that determines the blade mounting position, 4 partition plate, 5 skew angle, 6 casing, 7 air blowing nozzle, 8 air suction port,
9 heat exchanger, 10 stabilizer, 11 through-flow fan
Claims (8)
と、前記仕切板の間に複数の羽根を備え、羽根の取り付
け位置が以下の数１に示す式による間隔に配置すること
を特徴とする貫流送風羽根車。 【数１】 1. A plurality of partition plates perpendicular to a rotation axis, and a plurality of blades between the partition plates, wherein the blades are mounted at intervals according to the formula shown in the following formula 1. Once-through blower impeller. [Equation 1]
することを特徴とする請求項１記載の貫流送風羽根車。2. The cross flow fan impeller according to claim 1, wherein the cyclic order β is a natural number of 2 or more.
で、かつ偶数とすることを特徴とする請求項１記載の貫
流送風羽根車。3. The cross flow fan impeller according to claim 1, wherein the cyclic order β is a natural number of 2 or more and is even.
有理数とすることを特徴とする請求項１記載の貫流送風
羽根車。4. The cross flow fan impeller according to claim 1, wherein the arrangement angle variation amount α is a rational number in a range of 0 <α <1.
とする請求項１記載の貫流送風羽根車。5. The cross flow fan impeller according to claim 1, which is formed with a skew angle.
することを特徴とする請求項５記載の貫流送風羽根車。6. The cross flow fan impeller according to claim 5, wherein the cyclic order β is a natural number of 2 or more.
つ偶数とすることを特徴とする請求項５記載の貫流送風
羽根車。7. The once-through blower impeller according to claim 5, wherein the cyclic order β is a natural number of 2 or more and an even number.
有理数とすることを特徴とする請求項５記載の貫流送風
羽根車。8. The cross flow fan impeller according to claim 5, wherein the arrangement angle variation amount α is a rational number in the range of 0 <α <1.
Priority Applications (8)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP00644796A JP3484854B2 (en) | 1996-01-18 | 1996-01-18 | Once-through fan |
| DE69625322T DE69625322T2 (en) | 1996-01-18 | 1996-10-18 | Impeller for cross-flow fans |
| ES96307582T ES2191080T3 (en) | 1996-01-18 | 1996-10-18 | WHEEL FOR A CROSS CURRENT FAN. |
| EP96307582A EP0785362B1 (en) | 1996-01-18 | 1996-10-18 | Cross flow fan impeller |
| AU70557/96A AU680173B1 (en) | 1996-01-18 | 1996-11-01 | Cross flow fan impeller |
| KR1019970000872A KR100216104B1 (en) | 1996-01-18 | 1997-01-14 | Blower impeller |
| CN97102053A CN1076448C (en) | 1996-01-18 | 1997-01-15 | DC blasting vane wheel |
| HK97101945A HK1000496A1 (en) | 1996-01-18 | 1997-10-17 | Cross flow fan impeller |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP00644796A JP3484854B2 (en) | 1996-01-18 | 1996-01-18 | Once-through fan |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH09195979A JPH09195979A (en) | 1997-07-29 |
| JP3484854B2 true JP3484854B2 (en) | 2004-01-06 |
Family
ID=11638682
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP00644796A Expired - Lifetime JP3484854B2 (en) | 1996-01-18 | 1996-01-18 | Once-through fan |
Country Status (8)
| Country | Link |
|---|---|
| EP (1) | EP0785362B1 (en) |
| JP (1) | JP3484854B2 (en) |
| KR (1) | KR100216104B1 (en) |
| CN (1) | CN1076448C (en) |
| AU (1) | AU680173B1 (en) |
| DE (1) | DE69625322T2 (en) |
| ES (1) | ES2191080T3 (en) |
| HK (1) | HK1000496A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2015098700A1 (en) | 2013-12-27 | 2015-07-02 | ダイキン工業株式会社 | Multi-blade fan |
Families Citing this family (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| TW377393B (en) * | 1998-03-30 | 1999-12-21 | Sanyo Electric Co | Air coondition |
| KR100315518B1 (en) * | 1999-09-10 | 2001-11-30 | 윤종용 | Crossflow fan for an air conditioner |
| JP4075264B2 (en) * | 2000-01-28 | 2008-04-16 | セイコーエプソン株式会社 | Axial fan, centrifugal fan, and electronic equipment using them |
| JPWO2004029463A1 (en) * | 2002-09-24 | 2006-01-26 | 東芝キヤリア株式会社 | Cross-flow fan and air conditioner equipped with the same |
| CN100501170C (en) * | 2006-09-11 | 2009-06-17 | 广东科龙电器股份有限公司 | Through-flow fan impeller |
| US8881396B2 (en) | 2011-02-07 | 2014-11-11 | Revcor, Inc. | Method of manufacturing a fan assembly |
| EP2696078B1 (en) * | 2012-08-09 | 2019-10-02 | MTU Aero Engines AG | Bladed rotor for a turbomachine and corresponding assembly method |
| JP6601994B2 (en) * | 2013-09-06 | 2019-11-06 | 日立ジョンソンコントロールズ空調株式会社 | Indoor unit of air conditioner and air conditioner using the same |
| US9995316B2 (en) | 2014-03-11 | 2018-06-12 | Revcor, Inc. | Blower assembly and method |
| CN104153905B (en) * | 2014-08-04 | 2016-08-17 | 绿田机械股份有限公司 | A kind of air-cooled inclined type diesel engine |
| CN104132004B (en) * | 2014-08-04 | 2016-08-24 | 绿田机械股份有限公司 | A kind of cooling fan of use for diesel engine |
| CN105020176A (en) * | 2015-08-20 | 2015-11-04 | 珠海格力电器股份有限公司 | Fan blade and centrifugal fan |
| CN106837859B (en) * | 2017-02-13 | 2019-11-29 | 美的集团股份有限公司 | Draught fan impeller and centrifugal blower |
| CN108916078A (en) * | 2018-07-16 | 2018-11-30 | 大连碧蓝节能环保科技有限公司 | Helical blade centrifugal blower |
| US11274677B2 (en) | 2018-10-25 | 2022-03-15 | Revcor, Inc. | Blower assembly |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2322734A1 (en) * | 1973-05-05 | 1974-11-21 | Buderus Eisenwerk | FAN |
| JPS6017296A (en) | 1983-07-08 | 1985-01-29 | Matsushita Electric Ind Co Ltd | Vane wheel of crossing current blower |
| JP3349722B2 (en) * | 1992-08-25 | 2002-11-25 | 東芝キヤリア株式会社 | Indoor unit of air conditioner and packing method thereof |
| US5266007A (en) * | 1993-03-01 | 1993-11-30 | Carrier Corporation | Impeller for transverse fan |
| KR970009834B1 (en) * | 1994-02-08 | 1997-06-18 | 엘지전자 주식회사 | Impeller of cross fan |
| DE4421604C1 (en) * | 1994-06-21 | 1995-04-13 | Siemens Ag | Side-passage compressor |
| JPH0890397A (en) * | 1994-09-21 | 1996-04-09 | Kawasaki Steel Corp | Grinding structure for detecting minute defect in steel plate |
-
1996
- 1996-01-18 JP JP00644796A patent/JP3484854B2/en not_active Expired - Lifetime
- 1996-10-18 EP EP96307582A patent/EP0785362B1/en not_active Expired - Lifetime
- 1996-10-18 ES ES96307582T patent/ES2191080T3/en not_active Expired - Lifetime
- 1996-10-18 DE DE69625322T patent/DE69625322T2/en not_active Expired - Lifetime
- 1996-11-01 AU AU70557/96A patent/AU680173B1/en not_active Expired
-
1997
- 1997-01-14 KR KR1019970000872A patent/KR100216104B1/en active IP Right Grant
- 1997-01-15 CN CN97102053A patent/CN1076448C/en not_active Expired - Lifetime
- 1997-10-17 HK HK97101945A patent/HK1000496A1/en not_active IP Right Cessation
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2015098700A1 (en) | 2013-12-27 | 2015-07-02 | ダイキン工業株式会社 | Multi-blade fan |
| US10138903B2 (en) | 2013-12-27 | 2018-11-27 | Daikin Industries, Ltd. | Multi-blade fan |
Also Published As
| Publication number | Publication date |
|---|---|
| HK1000496A1 (en) | 2003-04-25 |
| CN1076448C (en) | 2001-12-19 |
| EP0785362A1 (en) | 1997-07-23 |
| KR970059509A (en) | 1997-08-12 |
| EP0785362B1 (en) | 2002-12-11 |
| KR100216104B1 (en) | 1999-08-16 |
| CN1164619A (en) | 1997-11-12 |
| ES2191080T3 (en) | 2003-09-01 |
| DE69625322T2 (en) | 2003-10-16 |
| AU680173B1 (en) | 1997-07-17 |
| JPH09195979A (en) | 1997-07-29 |
| DE69625322D1 (en) | 2003-01-23 |
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