JP6709899B2 - Blower fan and blower unit using the same - Google Patents
Blower fan and blower unit using the same Download PDFInfo
- Publication number
- JP6709899B2 JP6709899B2 JP2016062990A JP2016062990A JP6709899B2 JP 6709899 B2 JP6709899 B2 JP 6709899B2 JP 2016062990 A JP2016062990 A JP 2016062990A JP 2016062990 A JP2016062990 A JP 2016062990A JP 6709899 B2 JP6709899 B2 JP 6709899B2
- Authority
- JP
- Japan
- Prior art keywords
- main plate
- fan
- blower
- blade
- blower fan
- 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.)
- Active
Links
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
Description
本発明は遠心ターボ式の送風ファンおよび、当該送風ファンとファンケースとモータを備える送風ユニットに関するものである。 The present invention relates to a centrifugal turbo blower fan and a blower unit including the blower fan, a fan case, and a motor.
従来の遠心ターボ式の送風ファンとしては、図１１および図１２に示すようなものが知られている。図１１の送風ファンは、モータの回転軸が固定される主板５４と、主板５４に対向配置された副板５２と、主板５４と副板５２との間に配置されるファン羽根５３を備えている。モータの回転と共に送風ファンを反時計回りの方向に回転させると、副板５２の開口へと空気が吸引され、ファン羽根５３の後縁部に向かって放射状に空気が吐出されるようになっている。 As a conventional centrifugal turbo blower fan, ones shown in FIGS. 11 and 12 are known. The blower fan of FIG. 11 includes a main plate 54 to which the rotation shaft of the motor is fixed, a sub plate 52 opposed to the main plate 54, and fan blades 53 arranged between the main plate 54 and the sub plate 52. There is. When the blower fan is rotated counterclockwise along with the rotation of the motor, air is sucked into the opening of the sub plate 52 and is radially discharged toward the rear edge of the fan blade 53. There is.
ファン羽根５３の副板５２側後縁部に切欠き部５５が設けられ、ファン羽根５３と副板５２との間に隙間を持たせるようにしている。この隙間により、局所的な流速の増加やケースの舌部との圧力変動値を低減し、羽根通過周波数を減少させている。そして、切欠き部５５の位置は翼性能の低い部位であるため、隙間を有していても送風性能が低下することはほぼない（特許文献１参照）。 A cutout portion 55 is provided at a rear edge portion of the fan blade 53 on the side of the sub plate 52 so that a gap is provided between the fan blade 53 and the sub plate 52. Due to this gap, the local flow velocity is increased, the pressure fluctuation value with the tongue of the case is reduced, and the blade passing frequency is reduced. Further, since the position of the cutout portion 55 is a portion where the blade performance is low, even if there is a gap, the air blowing performance is hardly deteriorated (see Patent Document 1).
図１２の送風ファンは、前記同様に羽根通過周波数を減少させるものであるが、ファン羽根６３の主板６４側の後縁部に切欠き部６５を設けている。切り欠き部６５によりケース近傍を通過するときに発生する圧力変動値を低減させ、羽根通過周波数を低減させている（特許文献２参照）。 The blower fan shown in FIG. 12 reduces the blade passing frequency in the same manner as described above, but has a cutout portion 65 at the rear edge of the fan blade 63 on the main plate 64 side. The notch portion 65 reduces the pressure fluctuation value that occurs when passing near the case, and reduces the blade passing frequency (see Patent Document 2).
送風ユニットにおいて、低騒音化の達成の為には、送風ファンとファンケースにおける要因が大きく、送風ファンおよびファンケースの形状によって騒音改善をしていくことが可能である。一般的には低騒音化において、送風ファンとファンケースの舌部との距離は、ファン外径の１０％程度は確保しなければならない。ファンケースの大きさ制限により、送風ファンとファンケース間の距離をファン外径の１０％以上を確保できない場合は、騒音問題が起こりうる可能性がある。しかし、送風ファンとファンケース間の距離を広げると騒音の改善は可能であるが、送風能力は低下するという課題がある。 In order to achieve low noise in the blower unit, there are many factors in the blower fan and the fan case, and noise can be improved by the shapes of the blower fan and the fan case. Generally, in order to reduce noise, the distance between the blower fan and the tongue of the fan case must be secured at about 10% of the outer diameter of the fan. Due to the size limitation of the fan case, if the distance between the blower fan and the fan case cannot be 10% or more of the outer diameter of the fan, a noise problem may occur. However, although the noise can be improved by increasing the distance between the blower fan and the fan case, there is a problem that the blowing ability is reduced.
特許文献１および２に開示された送風ファンは、送風能力を低減させることなくファン騒音を低減する事が可能であるが、その為には副板の構成が必須となっている。 The blower fans disclosed in Patent Documents 1 and 2 can reduce the fan noise without reducing the blowing ability, but for that purpose, the construction of the auxiliary plate is essential.
本発明は、前記従来の課題に鑑みてなされたもので、副板が無い送風ファンの構成で低騒音効果があり、主板の形状についても制限がなく、ファン外径の１０％以下しか送風ファンとファンケース間の距離が確保できない場合でも低騒音効果をはかれる、送風ユニットを提供することを目的とする。 The present invention has been made in view of the above-mentioned conventional problems, and has a low noise effect in a configuration of a blower fan without a sub-plate, and there is no limitation on the shape of the main plate, and the blower fan has a fan outer diameter of 10% or less. It is an object of the present invention to provide a blower unit that achieves a low noise effect even when the distance between the fan case and the fan case cannot be secured.
上記の目的を達成するため、本発明の送風ファンは、回転軸が固定される主板と、主板の回転方向に対して中央部よりも両端部が後ろに位置するように湾曲し、回転方向の反対方向に向かって主板から突き出た後縁部を含む複数枚の羽根を有し、後縁部の前記主板側に欠部を設けるとともに、前記羽根の前記主板が位置する反対側を開放としたことを特徴とする。欠部の大きさは、羽根の主板側の最小径をｃ、前記羽根の最大径をｄとすると、０．８＜（ｃ／ｄ）＜０．９６であることが望ましい。また欠部の高さは、羽根の最大径を境として、主板側の寸法をａ、反主板側の寸法をｂとすると、１.０＜（ｂ／ａ）＜２．５であることが望ましい。 In order to achieve the above-mentioned object, the blower fan of the present invention has a main plate to which a rotating shaft is fixed and a main plate that is curved so that both ends are located rearward with respect to the central part in the rotational direction, and the rotational direction It has a plurality of blades including a rear edge portion protruding from the main plate in the opposite direction, and a notch is provided on the main plate side of the rear edge portion, and the opposite side of the blade where the main plate is located is open. It is characterized by The size of the notch is preferably 0.8<(c/d)<0.96, where c is the minimum diameter of the blade on the main plate side and d is the maximum diameter of the blade. The height of the cutout is 1.0<(b/a)<2.5, where a is the dimension on the main plate side and b is the dimension on the side opposite the main plate with the maximum diameter of the blade as the boundary. desirable.
また、本発明の送風ユニットは、前述の送風ファンと、ファンケースと、モータを備えている。ファンケースは、主板のうち複数枚の羽根が位置する面と向かい合う吸込み口と、回転軸と交差する方向に位置する吹出口と、を有する。モータは、送風ファンを回転する。さらに送風ファンとファンケースの舌部の最短距離を、送風ファンの直径の１０％以下としている。 The blower unit of the present invention includes the blower fan described above, a fan case, and a motor. The fan case has a suction port that faces a surface of the main plate on which the plurality of blades are located, and a blowout port that is positioned in a direction intersecting the rotation axis. The motor rotates the blower fan. Further, the shortest distance between the blower fan and the tongue of the fan case is set to 10% or less of the diameter of the blower fan.
この構成により、ほぼ送風能力を低下させることなく、羽根通過周波数を低減させることで騒音性能の向上がはかれる。そしてファンとファンケース舌部間の距離がファン外径の１０％以下である場合に顕著な効果を発揮できる。 With this configuration, noise performance can be improved by reducing the blade passing frequency without substantially reducing the blowing capacity. A remarkable effect can be exhibited when the distance between the fan and the tongue of the fan case is 10% or less of the outer diameter of the fan.
本発明によれば、副板を構成しない送風ファンを使用する送風ユニットで、送風能力を低下させる事なく低騒音化を達成できる。 According to the present invention, a blower unit that uses a blower fan that does not form a sub-plate can achieve low noise without lowering the blowing ability.
以下、本発明における実施形態を図１〜図４にしたがって説明する。 Hereinafter, embodiments of the present invention will be described with reference to FIGS.
図１は送風ユニットの構成図であり、図２はその断面図である。図３は本実施形態における送風ファンの斜視図で、図４は、その送風ファンの側面視の概略図である。 FIG. 1 is a configuration diagram of a blower unit, and FIG. 2 is a sectional view thereof. FIG. 3 is a perspective view of the blower fan of this embodiment, and FIG. 4 is a schematic side view of the blower fan.
送風ユニットは、少なくとも、蝸牛形状のファンケース１０と、内部に構成される空気流路をモータ１４により回転駆動される送風ファン１１とで構成される。送風ファン１１の回転により、吸込み口１３から空気を吸い込み、その吸い込んだ空気を吹出口１２へと吐き出す。このような送風ユニットは、例えば、冷蔵庫内の冷気を循環させる空気循環経路に搭載すれば、なんらかの冷却手段と組み合わせる事により、冷蔵庫の庫内を冷やすことができる。 The blower unit is composed of at least a cochlear fan case 10 and a blower fan 11 whose inner air flow path is driven to rotate by a motor 14. By the rotation of the blower fan 11, air is sucked from the suction port 13 and the sucked air is discharged to the air outlet 12. If such a blower unit is mounted on, for example, an air circulation path for circulating cold air in the refrigerator, the inside of the refrigerator can be cooled by combining it with some cooling means.
送風ファン１１は、図３に示すように、回転軸が固定された平坦な主板２１と、主板２
１に回転方向に対して後ろ向きに湾曲した複数枚のファン羽根２２を配置した、遠心式ターボファンとなっている。ファン羽根２２の主板側の後縁部に欠部２３が設けられ、主板２１の直径はファン羽根２２の最大外径よりも小さくなっている。なお、従来例のような副板は設けていない。
As shown in FIG. 3, the blower fan 11 includes a flat main plate 21 having a fixed rotating shaft and a main plate 2
1 is a centrifugal turbofan in which a plurality of fan blades 22 curved rearward with respect to the rotation direction are arranged. A notch 23 is provided at the rear edge of the fan blade 22 on the main plate side, and the diameter of the main plate 21 is smaller than the maximum outer diameter of the fan blade 22. It should be noted that a sub plate unlike the conventional example is not provided.
本実施形態では、ファンとファンケースの舌部１５の最も近くなる距離ｅ（図２参照）が、送風ファンの最大径ｄの１０％以下の５ｍｍとしており、騒音低減の為には距離ｅを最大径ｄの１０％以上とするべきであるという、広く知られているような構成とはなっていない。 In this embodiment, the distance e (see FIG. 2) that is the closest to the tongue portion 15 of the fan and the fan case is 5 mm that is 10% or less of the maximum diameter d of the blower fan, and the distance e is set to reduce noise. It does not have a widely known configuration that it should be 10% or more of the maximum diameter d.
以上のような構成により、羽根通過周波数音の原因であるファンケース近傍通過時の送風ファンとファンケース間に発生する圧力差を減少させることが可能となる。また、欠部の位置は羽根性能の低い部位であるため、欠部を有していても送風性能が低下することはほぼない。また送風ファン１１は板金で作成が可能であり、樹脂で作成する場合は、アンダーカット形状を必要としない構成なので低コストで製造できる。 With the above-described configuration, it is possible to reduce the pressure difference between the blower fan and the fan case when passing near the fan case, which is the cause of the blade passing frequency sound. Further, since the position of the cutout portion is a portion where the blade performance is low, even if the cutout portion has the cutout portion, the blowing performance is hardly deteriorated. The blower fan 11 can be made of sheet metal, and when made of resin, it can be manufactured at low cost because it does not require an undercut shape.
上記のように構成された送風ファンおよびこれを用いた送風ユニットについて詳細に説明する。 The blower fan configured as described above and the blower unit using the blower fan will be described in detail.
送風ファン１１の中心部から流入してきた空気は複数個設けたファン羽根２２間に流入する際、ファン羽根２２に沿って風は後縁側へ流れる。 When the air that has flowed in from the center of the blower fan 11 flows between the plurality of fan blades 22 provided, the air flows along the fan blades 22 toward the trailing edge side.
ここで図５に、本形態における送風ファンと、欠部を設けない場合の送風ファンのファン表面の風流れを数値流体解析（ＣＦＤ）を使用し解析を行った結果を示す。図５（ａ）が本形態における送風ファン、図５（ｂ）が欠部を設けない場合の送風ファンの流れを示している。 Here, FIG. 5 shows the results of analysis of the air flow on the fan surface of the blower fan according to the present embodiment and the fan surface of the blower fan in the case where the cutout portion is not provided by using the numerical fluid analysis (CFD). FIG. 5A shows the flow of the blower fan in the present embodiment, and FIG. 5B shows the flow of the blower fan when the cutout is not provided.
図５（ｂ）に示すように、ファン羽根２２の端でファン羽根の主板側では風の流れが少なくなっており、その部分に欠部を設けても送風性能の減少を最低限とすることができる。 As shown in FIG. 5(b), the flow of air is small at the end of the fan blades 22 on the main plate side of the fan blades, and even if a cutout is provided in that portion, the reduction of the blowing performance should be minimized. You can
本実施の形態では、ファン羽根の端とファンケースが最も近くなるファン羽根の最下部において、ファン羽根に欠部を設けているので、ファンとファンケース間の空間（距離ｅに相当）を大きくする事ができ、その結果ファンとファンケース間の圧力を減少できる。 In the present embodiment, since the fan blade has a cutout at the bottom of the fan blade where the end of the fan blade is closest to the fan case, the space between the fan and the fan case (corresponding to the distance e) is increased. It is possible to reduce the pressure between the fan and the fan case as a result.
送風ファンがファンケースの舌部を通過するたびに発生する圧力差が羽根通過周波数音となる事は分かっており、圧力変動を少なくすることは羽根通過周波数音の低減に効果的である。 It is known that the pressure difference generated every time the blower fan passes through the tongue portion of the fan case becomes the blade passing frequency sound, and reducing the pressure fluctuation is effective for reducing the blade passing frequency sound.
図４に示すように、本実施の形態における欠部２３の大きさは、欠部の最小径ｃ（主板の直径に相当）と、ファン羽根２２の最大径ｄとの比で示すと、０．８＜（ｃ／ｄ）＜０．９６としている。また、欠部２３の高さは、ファン羽根の最大径となる点を境として、その上部寸法ａと下部寸法ｂとの比で示すと、１．０＜（ｂ／ａ）＜２．５としている。 As shown in FIG. 4, the size of the cutout 23 in the present embodiment is 0 when expressed by the ratio of the minimum diameter c of the cutout (corresponding to the diameter of the main plate) and the maximum diameter d of the fan blades 22. .8<(c/d)<0.96. Further, the height of the cutout 23 is 1.0<(b/a)<2.5 when it is represented by the ratio of the upper dimension a and the lower dimension b of the fan blade, with the maximum diameter of the fan blade as a boundary. I am trying.
双方ともこの範囲を超えると、羽根通過周波数騒音に対しては効果が期待できるが、送風ファンとしての送風性能の低下を招く恐れがあり、結果としてファン回転数の増大化・ファン効率の低下が避けられなくなる。 If both exceed this range, an effect can be expected with respect to blade passing frequency noise, but there is a risk that the blowing performance of the blower fan will be reduced, resulting in an increase in fan speed and a decrease in fan efficiency. Inevitable.
図６は、ｃ／ｄの比率と、送風ユニットより送風できる静圧の変化を示したグラフである。ｃ／ｄが０．８以下となると、発生する静圧がｃ／ｄが０．９６時の静圧を基準とす
ると、約２割の低下となり送風性能が大きく低下する事となる。ｃ／ｄが０．９６以上となるとファンとファンケース間の圧力が乏しく上昇するので好ましくない。
FIG. 6 is a graph showing changes in the ratio of c/d and the static pressure that can be blown by the blower unit. When c/d is 0.8 or less, the generated static pressure is about 20% lower than the static pressure when c/d is 0.96, and the air blowing performance is significantly reduced. When c/d is 0.96 or more, the pressure between the fan and the fan case rises poorly, which is not preferable.
ファンとケース間の圧力が高い状態であると、騒音が大きくなる傾向がある。図７に、ｃ／ｄが０．９５の場合と、０．９８の場合の圧力状態を示す。４［Ｐａ］以上の圧力箇所を黒く塗りつぶしている。０．９８の場合は圧力上昇の領域が大きくなっているのがわかる。 When the pressure between the fan and the case is high, noise tends to increase. FIG. 7 shows pressure states when c/d is 0.95 and when it is 0.98. Pressure points of 4 [Pa] or more are painted black. In the case of 0.98, it can be seen that the region of pressure increase is large.
次に、図８は、ｂ／ａの比率と、送風ユニットより送風できる風量の変化を示したグラフである。ｂ／ａが１．０以下となると、発生する風量がｂ／ａが２．５の時の風量を基準とすると、約２割の低下となり送風性能が大きく低下する事となる。ｂ／ａが２．５以上となるとファンとファンケース間の圧力が乏しく上昇するため好ましくない。 Next, FIG. 8 is a graph showing a change in b/a ratio and the amount of air that can be blown from the blowing unit. When b/a is 1.0 or less, the generated air volume is about 20% lower than the air volume when b/a is 2.5, and the air blowing performance is significantly reduced. When b/a is 2.5 or more, the pressure between the fan and the fan case rises poorly, which is not preferable.
ファンとケース間の圧力が高い状態であると、騒音が大きくなる。図９では、ｂ／ａの比率が２．３３の場合と、３．０の場合の圧力状態を示す。５［Ｐａ］以上の圧力箇所を黒く塗りつぶしている。３．０の場合が圧力上昇の領域が大きくなっているのがわかる。 When the pressure between the fan and the case is high, the noise becomes loud. FIG. 9 shows pressure states when the b/a ratio is 2.33 and when it is 3.0. The pressure points of 5 [Pa] or more are painted black. It can be seen that the region of pressure increase is large in the case of 3.0.
ここで、本実施形態における騒音特性結果を図１０に示す。図１０（ａ）は、ｃ／ｄ＝０．９５、ｂ／ａ＝２．３の本形態の送風ファンを用いた場合の結果であり、図１０（ｂ）は、欠部のない送風ファンを用いた場合の結果である。ファン羽根の枚数が１３枚、回転数は１５８０ｒｐｍであるため、ＮＺ成分である３４０Ｈｚ近傍に羽根通過周波数が存在する。３４０Ｈｚは、ファン羽根の枚数１３枚×１５８０ｒｐｍ／６０（ｒｐｓ）により算出する。 Here, the noise characteristic result in this embodiment is shown in FIG. FIG. 10A shows the result when the blower fan of this embodiment with c/d=0.95 and b/a=2.3 is used, and FIG. 10B shows a blower fan with no cuts. Is the result when is used. Since the number of fan blades is 13 and the rotation speed is 1580 rpm, the blade passing frequency exists near 340 Hz which is the NZ component. 340 Hz is calculated by the number of fan blades 13×1580 rpm/60 (rps).
図に示すように、欠部のない送風ファンを用いた場合にくらべて、本形態の送風ファンを用いた場合は、約５ｄＢ（Ａ）の騒音削減効果が得られた。 As shown in the figure, when the blower fan of this embodiment was used, a noise reduction effect of about 5 dB(A) was obtained as compared with the case of using the blower fan having no cutouts.
本発明の送風ユニットは、冷蔵庫や空気調和機などの各種電気機器の送風ユニットに適用することができる。 The blower unit of the present invention can be applied to blower units of various electric devices such as refrigerators and air conditioners.
１０ ファンケース
１１ 送風ファン
１２ 吹出口
１３ 吸込み口
１４ モータ
１５ 舌部
２１ 主板
２２ ファン羽根
２３ 欠部
10 Fan Case 11 Blower Fan 12 Outlet 13 Suction Port 14 Motor 15 Tongue 21 Main Plate 22 Fan Blade 23 Missing
Claims (6)
前記主板のうち前記複数枚の羽根が位置する面と向かい合う吸込み口と、前記回転軸と交差する方向に位置する吹出口と、を有するファンケースと、
前記送風ファンを回転するモータと、を備え、
前記送風ファンと前記ファンケースの舌部の最短距離が、前記送風ファンの直径の１０％以下であることを特徴とする送風ユニット。 A main plate to which a rotary shaft is fixed, and a rear edge portion that is curved so that both end portions are located behind the central portion with respect to the rotation direction of the main plate, and that protrudes from the main plate in a direction opposite to the rotation direction. Having a plurality of blades, including a notch on the side of the main plate of the trailing edge, and a blower fan that opens the opposite side of the blade where the main plate is located ,
A fan case having a suction port facing a surface of the main plate on which the plurality of blades are positioned, and a blower port positioned in a direction intersecting the rotation axis ,
And a motor for rotating the blowing fan,
A blower unit, wherein the shortest distance between the blower fan and the tongue of the fan case is 10% or less of the diameter of the blower fan .
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2016062990A JP6709899B2 (en) | 2016-03-28 | 2016-03-28 | Blower fan and blower unit using the same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2016062990A JP6709899B2 (en) | 2016-03-28 | 2016-03-28 | Blower fan and blower unit using the same |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2017180094A JP2017180094A (en) | 2017-10-05 |
| JP6709899B2 true JP6709899B2 (en) | 2020-06-17 |
Family
ID=60003907
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2016062990A Active JP6709899B2 (en) | 2016-03-28 | 2016-03-28 | Blower fan and blower unit using the same |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP6709899B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112065749A (en) * | 2020-09-14 | 2020-12-11 | 德州丙田机电科技有限公司 | Impeller |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108661929B (en) * | 2018-04-28 | 2021-05-14 | 青岛海信日立空调***有限公司 | Centrifugal fan and ceiling embedded air conditioner indoor unit |
| US20240200569A1 (en) * | 2020-03-24 | 2024-06-20 | Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. | Impeller of centrifugal compressor, centrifugal compressor including the impeller, and method for producing the impeller |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4930981A (en) * | 1989-08-18 | 1990-06-05 | Walker Manufacturing Company | Low noise impeller |
| DE69315484T2 (en) * | 1992-06-23 | 1998-06-04 | Koninkl Philips Electronics Nv | Polarization-sensitive beam splitter, method for producing such a magneto-optical scanning device with such a beam splitter |
| JP2002371997A (en) * | 2001-06-13 | 2002-12-26 | Denso Corp | Centrifugal blower |
| FI122563B (en) * | 2005-02-21 | 2012-03-30 | Flaekt Woods Ab | Centrifugal Impeller |
| JP5119351B2 (en) * | 2011-06-14 | 2013-01-16 | 日立アプライアンス株式会社 | Drum dryer |
| JP6078945B2 (en) * | 2011-11-04 | 2017-02-15 | ダイキン工業株式会社 | Centrifugal blower |
| JP2015095962A (en) * | 2013-11-12 | 2015-05-18 | 株式会社東芝 | Rotary machine |
-
2016
- 2016-03-28 JP JP2016062990A patent/JP6709899B2/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112065749A (en) * | 2020-09-14 | 2020-12-11 | 德州丙田机电科技有限公司 | Impeller |
| CN112065749B (en) * | 2020-09-14 | 2021-09-24 | 德州丙田机电科技有限公司 | Impeller |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2017180094A (en) | 2017-10-05 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| AU2014357992C1 (en) | Blower and outdoor unit of air conditioner comprising same | |
| EP3034885B1 (en) | Centrifugal fan and air conditioner provided with the same | |
| CN101990604A (en) | Centrifugal fan | |
| AU2014238673B2 (en) | Centrifugal fan and air conditioner having the same | |
| JPWO2017060987A1 (en) | Blower and air conditioner equipped with the same | |
| JP5744209B2 (en) | Air conditioner | |
| JP6709899B2 (en) | Blower fan and blower unit using the same | |
| JP4894900B2 (en) | Blower fan and blower using the same | |
| JP2007205268A (en) | Centrifugal fan | |
| CN110506164B (en) | Propeller fan and outdoor unit for air conditioner | |
| WO2020110967A1 (en) | Propeller fan | |
| JP2015117605A (en) | Centrifugal blower | |
| JP2009085533A (en) | Air conditioner | |
| JP6330738B2 (en) | Centrifugal blower and air conditioner using the same | |
| JP4994433B2 (en) | Sirocco fan and air conditioner indoor unit using this sirocco fan | |
| JP2016160905A (en) | Centrifugal fan | |
| WO2020110968A1 (en) | Propeller fan | |
| JP7088309B2 (en) | Propeller fan | |
| JP2010236426A (en) | Sirocco fan | |
| JP2012202362A (en) | Impeller, and centrifugal fan including the same | |
| JP2012117387A (en) | Air blower and air conditioner equipped with the air blower | |
| WO2018042689A1 (en) | Air conditioner | |
| JP2015214912A (en) | Axial flow fan and air conditioner with axial flow fan | |
| JP2007162465A (en) | Turbo fan and air conditioner using the same | |
| WO2022209551A1 (en) | Blower and indoor unit |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20160329 |
|
| RD01 | Notification of change of attorney |
Free format text: JAPANESE INTERMEDIATE CODE: A7421 Effective date: 20160526 |
|
| A621 | Written request for application examination |
Free format text: JAPANESE INTERMEDIATE CODE: A621 Effective date: 20180910 |
|
| RD01 | Notification of change of attorney |
Free format text: JAPANESE INTERMEDIATE CODE: A7421 Effective date: 20190118 |
|
| A131 | Notification of reasons for refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A131 Effective date: 20190625 |
|
| A977 | Report on retrieval |
Free format text: JAPANESE INTERMEDIATE CODE: A971007 Effective date: 20190627 |
|
| A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20190823 |
|
| A131 | Notification of reasons for refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A131 Effective date: 20200114 |
|
| A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20200312 |
|
| TRDD | Decision of grant or rejection written | ||
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 20200407 |
|
| A61 | First payment of annual fees (during grant procedure) |
Free format text: JAPANESE INTERMEDIATE CODE: A61 Effective date: 20200420 |
|
| R151 | Written notification of patent or utility model registration |
Ref document number: 6709899 Country of ref document: JP Free format text: JAPANESE INTERMEDIATE CODE: R151 |