JP2769211B2 - Blower - Google Patents
BlowerInfo
- Publication number
- JP2769211B2 JP2769211B2 JP1307936A JP30793689A JP2769211B2 JP 2769211 B2 JP2769211 B2 JP 2769211B2 JP 1307936 A JP1307936 A JP 1307936A JP 30793689 A JP30793689 A JP 30793689A JP 2769211 B2 JP2769211 B2 JP 2769211B2
- Authority
- JP
- Japan
- Prior art keywords
- orifice
- impeller
- axial
- blower
- distance
- 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
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- Structures Of Non-Positive Displacement Pumps (AREA)
Description
【発明の詳細な説明】 産業上の利用分野 本発明は、主にセパレート型空気調和器の室外機など
に用いられる送風機に関するものである。Description: TECHNICAL FIELD The present invention relates to a blower mainly used for an outdoor unit of a separate type air conditioner.
従来の技術 従来この種の送風機ではオリフィスの断面形状は実開
昭62−1054320号公報などで提案されているように各部
分が同一の形状とするのが一般的であった。2. Description of the Related Art Conventionally, in this type of blower, the cross-sectional shape of an orifice generally has the same shape in each part as proposed in Japanese Utility Model Laid-Open No. 62-1054320.
以下図面を参照しながら上述した従来の送風機の一例
について説明する。Hereinafter, an example of the above-described conventional blower will be described with reference to the drawings.
第４図，第５図は従来の送風機を搭載したセパレート
型空気調和機の室外機の構造を示すものであり、さらに
第６図，第７図は従来の送風機のオリフィスの断面形状
を示すものである。4 and 5 show the structure of an outdoor unit of a separate type air conditioner equipped with a conventional blower, and FIGS. 6 and 7 show cross-sectional shapes of orifices of the conventional blower. It is.
１は室外機本体であり、送風機室２および機械室３に
分割されている。送風機室２は略長方形の前面パネル４
と側板５および背面部に設置した熱交換器６によって形
成されている。また、送風機室２内には軸流羽根車７を
配設し、前記前面パネル４の略中央部にはオリフィス８
が配設してあり、オリフィス８内に前記軸流羽根車７の
先端部を挿入してある。Reference numeral 1 denotes an outdoor unit main body, which is divided into a blower room 2 and a machine room 3. The blower room 2 has a substantially rectangular front panel 4
And a side plate 5 and a heat exchanger 6 installed on the back. An axial impeller 7 is provided in the blower room 2, and an orifice 8 is provided substantially at the center of the front panel 4.
The tip of the axial impeller 7 is inserted into the orifice 8.
以上のように構成された送風機について、以下その動
作を説明する。The operation of the blower configured as described above will be described below.
軸流羽根車７が回転すると熱交換器６を介して空気が
送風機室内２に流入し、この際外気と熱交換器６との間
で熱交換がなされる。送風機室２内に流入した空気は軸
流羽根車７の送風作用でオリフィス８を介して送風機室
２外に吐出される。When the axial impeller 7 rotates, air flows into the blower chamber 2 via the heat exchanger 6, and at this time, heat is exchanged between the outside air and the heat exchanger 6. The air flowing into the blower chamber 2 is discharged to the outside of the blower chamber 2 through the orifice 8 by the blowing action of the axial impeller 7.
発明が解決しようとする課題 しかしながら、上記のような構成では前面パネル４が
長方形のため、前面パネルの長辺側の断面（Ａ−Ａ）で
は第６図に示すように軸流羽根車７と側壁5aとの距離が
大きく、軸流羽根車７に対して求心方向成分の多い流入
気流Ｅが発生する。However, since the front panel 4 is rectangular in the above-described configuration, the axial impeller 7 and the cross section (A-A) on the long side of the front panel as shown in FIG. The distance from the side wall 5a is large, and an inflow airflow E having a large centripetal component is generated with respect to the axial impeller 7.
一方、前面パネルの矩辺側の断面（Ｂ−Ｂ）では第７
図に示すように軸流羽根車７と側壁5bとの距離が小さ
く、軸流羽根車７に対して軸流方向成分の多い流入気流
Ｆが発生する。このように、軸流羽根車７のオリフィス
付近の流入気流の方向はオリフィス８の各部位によって
異なるのに対して、オリフィス８の断面形状は各部同一
であるため、流入気流したオリフィス形状が適合してい
ない部分があった。例えば、第６図で示すように前面パ
ネルの長辺側の断面では、求心方向成分の多い流入気流
Ｅに対し、オリフィス８の吸入側先端部8aの曲げ曲率R1
が大き過ぎ流れの剥離が生じやすく、この気流の剥離に
より乱流音が増加し、送風騒音が増加するという問題点
があり、オリフィス８近傍での流れの剥離を防止するこ
とが課題となっていた。On the other hand, in the cross section (BB) on the rectangular side of the front panel, the seventh
As shown in the figure, the distance between the axial flow impeller 7 and the side wall 5b is small, and an inflow airflow F having a large axial flow direction component is generated with respect to the axial flow impeller 7. As described above, the direction of the inflow airflow in the vicinity of the orifice of the axial impeller 7 differs depending on each portion of the orifice 8, whereas the cross-sectional shape of the orifice 8 is the same, so that the shape of the orifice into which the inflow airflow conforms. There was no part. For example, as shown in FIG. 6, in the cross section on the long side of the front panel, the bending curvature R 1 of the suction-side tip 8a of the orifice 8 with respect to the inflow airflow E having a large centripetal component.
Is too large, and the separation of the flow is likely to occur, and the separation of the air flow increases the turbulent noise and increases the blowing noise. There is a problem in preventing the separation of the flow near the orifice 8. Was.
本発明は上記課題に鑑み、前面パネルを長方形に保っ
たうえで、軸流羽根車のオリフィス付近の異なった流入
気流角に対応するオリフィス形状を設定し、オリフィス
付近での流れの剥離の少ない低騒音の送風機を提供する
ものである。In view of the above problems, the present invention sets the orifice shape corresponding to different inflow airflow angles near the orifice of the axial flow impeller while keeping the front panel rectangular, and reduces the flow separation near the orifice. A noise blower is provided.
課題を解決するための手段 上記課題を解決するために本発明の送風機は、略長方
形の前面パネルとその側面を囲む複数の側板で送風機室
を形成し、前記前面パネルにオリフィスを配設し、前記
オリフィス内に軸流羽根車を挿入して成る送風機におい
て、前記軸流羽根車の外周端と前記側板との距離が相対
的に長い部分では、前記軸流羽根車の回転軸を含む平面
で前記オリフィスを切断したときの断面は、前記オリフ
ィスの吸入側先端部の曲げ曲率半径が相対的に大きく
て、前記オリフィスの吸入側先端と前記軸流羽根車の外
周端との距離が相対的に長く、前記軸流羽根車の外周端
と前記側板との距離が相対的に短い部分では、前記軸流
羽根車の回転軸を含む平面で前記オリフィスを切断した
ときの断面は、前記オリフィスの吸入側先端部の曲げ曲
率半径が相対的に小さくて、前記オリフィスの吸入側先
端と前記軸流羽根車の外周端との距離が相対的に短くな
るように構成したのである。Means to solve the problem In order to solve the above problems, the blower of the present invention is a blower chamber is formed by a substantially rectangular front panel and a plurality of side plates surrounding the side surface thereof, and an orifice is arranged in the front panel, In a blower having an axial impeller inserted into the orifice, in a portion where the distance between the outer peripheral end of the axial impeller and the side plate is relatively long, a plane including the rotation axis of the axial impeller is used. The cross section when the orifice is cut has a relatively large bending radius of curvature at the suction-side tip of the orifice, and the distance between the suction-side tip of the orifice and the outer peripheral end of the axial-flow impeller is relatively large. In a long part where the distance between the outer peripheral end of the axial flow impeller and the side plate is relatively short, a cross section of the orifice cut along a plane including the rotation axis of the axial flow impeller is formed by suction of the orifice. Side tip tune The radius of curvature is relatively small, and the distance between the suction end of the orifice and the outer peripheral end of the axial impeller is relatively short.
作用 本発明の送風機は、前面パネルの短辺側の側板付近の
ように軸流羽根車の外周端と側板との距離が相対的に長
く、軸流羽根車に対して求心方向成分の多い流入気流が
発生する部位では、軸流羽根車の回転軸を含む平面でオ
リフィスを切断したときの断面は、オリフィスの吸入側
先端部の曲げ曲率半径が相対的に大きくて、オリフィス
の吸入側先端と軸流羽根車の外周端との距離が相対的に
長くなっており、流入気流が無理なくオリフィスに沿っ
て流れ、オリフィス付近での気流の急激な曲折による気
流の剥離を防止し、乱流音の発生が抑制される。In the blower of the present invention, the distance between the outer peripheral end of the axial flow impeller and the side plate is relatively long, such as near the side plate on the short side of the front panel, and the inflow with a large centripetal component into the axial flow impeller At the location where airflow occurs, the cross-section of the orifice when cut along a plane containing the rotation axis of the axial impeller has a relatively large bending radius of curvature at the suction-side tip of the orifice, and has a larger radius than the orifice suction-side tip. The distance from the outer peripheral end of the axial impeller is relatively long, and the inflow airflow flows along the orifice without difficulty, preventing separation of the airflow due to sudden bending of the airflow near the orifice, and turbulent noise. Is suppressed.
一方、前面パネルの長辺側の側板付近のように軸流羽
根車の外周端と側板との距離が相対的に短く、軸流羽根
車に対して流入気流が軸流方向の成分が多くなる部位で
は、軸流羽根車の回転軸を含む平面でオリフィスを切断
したときの断面は、オリフィスの吸入側先端部の曲げ曲
率半径が相対的に小さくて、オリフィスの吸入側先端と
軸流羽根車の外周端との距離が相対的に短くなってお
り、流入気流はオリフィスに沿って流れ、オリフィスの
壁面から剥離する恐れがなく、そのため送風機室の短辺
方向の寸法を小さくすることができる。On the other hand, the distance between the outer peripheral end of the axial impeller and the side plate is relatively short, such as near the side plate on the long side of the front panel, and the inflow airflow has a large axial flow component relative to the axial impeller. In the section, when the orifice is cut along a plane including the rotation axis of the axial impeller, the bending radius of curvature of the orifice suction side tip is relatively small, and the orifice suction side tip and the axial flow impeller are cut. Is relatively short, and the inflow airflow flows along the orifice without being separated from the wall surface of the orifice, so that the dimension of the blower chamber in the short side direction can be reduced.
実 施 例 以下本発明の一実施例の送風機について図面を参照し
ながら説明する。尚、従来例と同一部分については同一
番号を符し、説明を省略する。Embodiment Hereinafter, a blower according to an embodiment of the present invention will be described with reference to the drawings. The same parts as those in the conventional example are denoted by the same reference numerals, and description thereof will be omitted.
第１図は本考案の一実施例における送風機を搭載した
セパレート型空気調和機の構造を示すものであり、第２
図は第１図のＣ−Ｃ線断面、第３図は第１図のＤ−Ｄ線
断面を示すものである。FIG. 1 shows the structure of a separate type air conditioner equipped with a blower according to an embodiment of the present invention.
The drawing shows a cross section taken along line CC of FIG. 1, and FIG. 3 shows a cross section taken along line DD of FIG.
４は略長方形の前面パネルで、その側面を囲む側板5
a,5bと共に送風機室２を形成し、前面パネル４にはオリ
フィス９を配設し、オリフィス９内に軸流羽根車７を挿
入して送風機を構成している。Reference numeral 4 denotes a substantially rectangular front panel, and a side plate 5 surrounding its side surface.
A blower chamber 2 is formed together with a and 5b, an orifice 9 is disposed on the front panel 4, and an axial impeller 7 is inserted into the orifice 9 to constitute a blower.
なお、第２図に示すように、軸流羽根車７の外周端と
側板5bとの距離が相対的に長い部分では、軸流羽根車７
の回転軸を含む平面でオリフィス９を切断したときの断
面は、オリフィス９の吸入側先端部9bの曲げ曲率半径R2
が相対的に大きくて、オリフィス９の吸入側先端と軸流
羽根車７の外周端との距離が相対的に長くなっている。As shown in FIG. 2, in the portion where the distance between the outer peripheral end of the axial flow impeller 7 and the side plate 5b is relatively long, the axial flow impeller 7
When the orifice 9 is cut along a plane including the rotation axis of the orifice 9, the bending radius of curvature R 2 of the suction-side tip 9 b of the orifice 9 is
Is relatively large, and the distance between the suction-side tip of the orifice 9 and the outer peripheral end of the axial impeller 7 is relatively long.
一方、第３図に示すように、軸流羽根車７の外周端と
側板5aとの距離が相対的に短い部分では、軸流羽根車７
の回転軸を含む平面でオリフィス９を切断したときの断
面は、オリフィス９の吸入側先端部9aの曲げ曲率半径R1
が相対的に小さくて、オリフィス９の吸入側先端と軸流
羽根車７の外周端との距離が相対的に短くなっている。On the other hand, as shown in FIG. 3, in the portion where the distance between the outer peripheral end of the axial impeller 7 and the side plate 5a is relatively short, the axial impeller 7
When the orifice 9 is cut along a plane including the rotation axis of the orifice 9, the bending radius of curvature R 1 of the suction-side tip 9 a of the orifice 9 is 1.
Is relatively small, and the distance between the front end of the orifice 9 on the suction side and the outer peripheral end of the axial impeller 7 is relatively short.
以上のように構成された送風機について、以下その動
作を説明する。軸流羽根車７が回転すると熱交換器６を
介して空気が送風機室内２に流入し、この際外気と熱交
換器６との間で熱交換がされる。送風機室２内に流入し
た空気は軸流羽根車７の送風作用でオリフィス９を介し
て送風機室２外に吐出される。The operation of the blower configured as described above will be described below. When the axial impeller 7 rotates, air flows into the blower chamber 2 via the heat exchanger 6, and at this time, heat is exchanged between the outside air and the heat exchanger 6. The air that has flowed into the blower chamber 2 is discharged out of the blower chamber 2 via the orifice 9 by the blowing action of the axial impeller 7.
ここで、前面パネルは長方形のため、前面パネルの長
辺側の断面（Ｃ−Ｃ）では第２図に示すように軸流羽根
車７の外周端と側板5bとの距離が相対的に長く、軸流羽
根車７に対して求心方向成分の多い流入気流Ｇが発生す
る。しかし、第２図に示すように、軸流羽根車７の回転
軸を含む平面でオリフィス９を切断したときの断面は、
オリフィス９の吸入側先端部9bの曲げ曲率半径R2が相対
的に大きくて、オリフィス９の吸入側先端と軸流羽根車
７の外周端との距離が相対的に長くなっているから、流
入気流がオリフィス９に沿って無理なくわん曲して流
れ、急激な曲折による気流剥離を起こすことがない。従
って、オリフィス付近での乱流の発生を抑え、乱流音に
よる送風騒音を低減することができる。Here, since the front panel is rectangular, the distance between the outer peripheral end of the axial flow impeller 7 and the side plate 5b is relatively long in the cross section (CC) of the long side of the front panel as shown in FIG. , An inflow airflow G having a large centripetal component with respect to the axial impeller 7 is generated. However, as shown in FIG. 2, the cross section when the orifice 9 is cut along a plane including the rotation axis of the axial impeller 7 is as follows.
Bend radius of curvature R 2 of the suction-side tip portion 9b of the orifice 9 is relatively large, since the distance between the outer peripheral edge of the suction side tip and axial flow impeller 7 of the orifice 9 is relatively long, the inflow The air flow is smoothly curved and flows along the orifice 9, and the air flow is not separated due to a sharp bend. Therefore, the generation of turbulence near the orifice can be suppressed, and blowing noise due to turbulence noise can be reduced.
また、前面パネルの短辺側の断面（Ｄ−Ｄ）では第３
図に示すように軸流羽根車７の外周端と側板5aとの距離
が相対的に短く、軸流羽根車７に対して軸流方向成分の
多い流入気流Ｈが発生する。しかし、第３図に示すよう
に、軸流羽根車７の回転軸を含む平面でオリフィス９を
切断したときの断面は、オリフィス９の吸入側先端部9a
の曲げ曲率半径R1が相対的に小さくして、オリフィス９
の吸入側先端と軸流羽根車７の外周端との距離が相対的
に短くなっており、流入気流はオリフィス９に沿って流
れ、オリフィス９の壁面から剥離する恐れがなく、送風
機室２の短辺方向の寸法を小さくすることができ、製品
寸法を小さくすることができる。In the section (DD) on the short side of the front panel, the third
As shown in the figure, the distance between the outer peripheral end of the axial flow impeller 7 and the side plate 5a is relatively short, and an inflow airflow H having a large axial flow component is generated with respect to the axial flow impeller 7. However, as shown in FIG. 3, when the orifice 9 is cut along a plane including the rotation axis of the axial impeller 7, the cross-section of the orifice 9 on the suction side tip 9a
The radius of curvature R 1 of the orifice 9
The distance between the suction-side tip and the outer peripheral end of the axial-flow impeller 7 is relatively short, and the inflow air flows along the orifice 9 without fear of separating from the wall surface of the orifice 9. The size in the short side direction can be reduced, and the product size can be reduced.
発明の効果 以上のように、本発明の送風機は、略長方形の前面パ
ネルとその側面を囲む複数の側板で送風機室を形成し、
前記前面パネルにオリフィスを配設し、前記オリフィス
内に軸流羽根車を挿入して成る送風機において、前記軸
流羽根車の外周端と前記側板との距離が相対的に長い部
分では、前記軸流羽根車の回転軸を含む平面で前記オリ
フィスを切断したときの断面は、前記オリフィスの吸入
側先端部の曲げ曲率半径が相対的に大きくて、前記オリ
フィスの吸入側先端と前記軸流羽根車の外周端との距離
が相対的に長く、前記軸流羽根車の外周端と前記側板と
の距離が相対的に短い部分では、前記軸流羽根車の回転
軸を含む平面で前記オリフィスを切断したときの断面
は、前記オリフィスの吸入側先端部の曲げ曲率半径が相
対的に小さくて、前記オリフィスの吸入側先端と前記軸
流羽根車の外周端との距離が相対的に短くなるように構
成したことにより、軸流羽根車の外周端と側板との距離
が相対的に長く、軸流羽根車に対して求心方向成分の多
い流入気流が発生する部位では、流入気流が無理なくオ
リフィスに沿って流れ、オリフィス付近での気流の急激
な曲折による気流の剥離を防止し、乱流音の発生が抑制
される。Effect of the Invention As described above, the blower of the present invention forms a blower chamber with a substantially rectangular front panel and a plurality of side plates surrounding the side surfaces thereof,
An orifice is provided on the front panel, and an axial impeller is inserted into the orifice.In a blower in which the distance between the outer peripheral end of the axial impeller and the side plate is relatively long, the shaft is When the orifice is cut along a plane including the rotation axis of the flow impeller, the cross-section of the orifice has a relatively large bending radius of curvature at the suction-side tip of the orifice. In a portion where the distance between the outer peripheral end of the axial flow impeller is relatively long and the distance between the outer peripheral end of the axial flow impeller and the side plate is relatively short, the orifice is cut along a plane including the rotation axis of the axial flow impeller. The cross section of the orifice is such that the bending radius of curvature of the suction side tip of the orifice is relatively small, and the distance between the suction side tip of the orifice and the outer peripheral end of the axial flow impeller is relatively short. By configuring, In the part where the distance between the outer peripheral end of the flow impeller and the side plate is relatively long, and the inflow airflow having a large centripetal component with respect to the axial impeller is generated, the inflow airflow flows along the orifice without difficulty, near the orifice. In this case, the separation of the air flow due to the sharp bending of the air flow is prevented, and the generation of turbulent noise is suppressed.
一方、軸流羽根車の外周端と側板との距離が相対的に
短く、軸流羽根車に対して流入気流が軸流方向の成分が
多くなる部位では、流入気流はオリフィスに沿って流
れ、オリィスの壁面から剥離する恐れがなく、そのため
送風機室の短辺方向の寸法を小さくすることができ、製
品寸法を小さくすることができる。On the other hand, at a portion where the distance between the outer peripheral end of the axial impeller and the side plate is relatively short and the inflow airflow has a large component in the axial flow direction with respect to the axial impeller, the inflow airflow flows along the orifice, There is no fear of peeling off from the wall surface of the orifice, so that the size of the blower room in the short side direction can be reduced, and the product size can be reduced.
第１図は本発明の一実施例における送風機を搭載したセ
パレート型空気調和機の正面図、第２図は第１図のＣ−
Ｃ部断面図、第３図は第１図のＤ−Ｄ部断面図、第４図
は従来の送風機を搭載したセパレート型空気調和機の正
面図、第５図は第４図の中央横断面図、第６図は第４図
のＡ−Ａ部断面図、第７図は第４図のＢ−Ｂ部断面図で
ある。 ２……送風機室、４……前面パネル、７……軸流羽根
車、９……オリフィス、9a……オリフィス吸入側先端
部。FIG. 1 is a front view of a separate type air conditioner equipped with a blower according to an embodiment of the present invention, and FIG.
FIG. 3 is a cross-sectional view of a part C, FIG. 3 is a cross-sectional view of a DD part of FIG. 1, FIG. 4 is a front view of a separate type air conditioner equipped with a conventional blower, and FIG. FIG. 6 is a sectional view taken along the line AA of FIG. 4, and FIG. 7 is a sectional view taken along the line BB of FIG. 2 ... blower room, 4 ... front panel, 7 ... axial flow impeller, 9 ... orifice, 9a ... orifice suction side tip.
───────────────────────────────────────────────────── フロントページの続き (58)調査した分野(Int.Cl.6，ＤＢ名) F04D 29/44 F04D 29/54──────────────────────────────────────────────────続 き Continued on the front page (58) Field surveyed (Int.Cl. 6 , DB name) F04D 29/44 F04D 29/54
Claims (1)
数の側板とで送風機室を形成し、前記前面パネルにオリ
フィスを配設し、前記オリフィス内に軸流羽根車を挿入
して成る送風機において、 前記軸流羽根車の外周端と前記側板との距離が相対的に
長い部分では、前記軸流羽根車の回転軸を含む平面で前
記オリフィスを切断したときの断面は、前記オリフィス
の吸入側先端部の曲げ曲率半径が相対的に大きくて、前
記オリフィスの吸入側先端と前記軸流羽根車の外周端と
の距離が相対的に長く、 前記軸流羽根車の外周端と前記側板との距離が相対的に
短い部分では、前記軸流羽根車の回転軸を含む平面で前
記オリフィスを切断したときの断面は、前記オリフィス
の吸入側先端部の曲げ曲率半径が相対的に小さくて、前
記オリフィスの吸入側先端と前記軸流羽根車の外周端と
の距離が相対的に短くなるように構成したことを特徴と
する送風機。1. A blower comprising a substantially rectangular front panel and a plurality of side plates surrounding side surfaces thereof, forming a blower chamber, arranging an orifice in the front panel, and inserting an axial impeller into the orifice. In the portion where the distance between the outer peripheral end of the axial flow impeller and the side plate is relatively long, a cross section of the orifice cut along a plane including the rotation axis of the axial flow impeller is formed by suction of the orifice. The bending radius of curvature of the side tip is relatively large, the distance between the suction-side tip of the orifice and the outer peripheral end of the axial flow impeller is relatively long, and the outer peripheral end of the axial flow impeller and the side plate. In the portion where the distance is relatively short, the cross section of the orifice when cut along a plane including the rotation axis of the axial impeller has a relatively small radius of curvature at the suction-side tip of the orifice, Inhalation of the orifice Blower, characterized in that the distance between the tip and the outer peripheral end of said axial flow impeller is configured such relatively shorter.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1307936A JP2769211B2 (en) | 1989-11-28 | 1989-11-28 | Blower |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1307936A JP2769211B2 (en) | 1989-11-28 | 1989-11-28 | Blower |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03168395A JPH03168395A (en) | 1991-07-22 |
| JP2769211B2 true JP2769211B2 (en) | 1998-06-25 |
Family
ID=17974958
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1307936A Expired - Lifetime JP2769211B2 (en) | 1989-11-28 | 1989-11-28 | Blower |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2769211B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2009130954A1 (en) | 2008-04-22 | 2009-10-29 | 三菱電機株式会社 | Blower and heat pump device using same |
| WO2010053037A1 (en) | 2008-11-04 | 2010-05-14 | 三菱電機株式会社 | Blower and heat pump utilizing said blower |
| JP2013096622A (en) * | 2011-10-31 | 2013-05-20 | Daikin Industries Ltd | Outdoor unit of air conditioner |
| US9062888B2 (en) | 2008-03-11 | 2015-06-23 | Mitsubishi Electric Corporation | Air conditioner |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH05133398A (en) * | 1991-11-12 | 1993-05-28 | Matsushita Electric Ind Co Ltd | Blower |
| JP4690682B2 (en) * | 2004-09-07 | 2011-06-01 | 三菱電機株式会社 | air conditioner |
| JP5791276B2 (en) * | 2010-12-24 | 2015-10-07 | 三菱電機株式会社 | Blower, outdoor unit and refrigeration cycle apparatus |
| US10982863B2 (en) | 2018-04-10 | 2021-04-20 | Carrier Corporation | HVAC fan inlet |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60197013A (en) * | 1984-03-21 | 1985-10-05 | Hitachi Ltd | Clamping circuit |
| JPS649479A (en) * | 1987-07-01 | 1989-01-12 | Fuji Xerox Co Ltd | One-component developing device |
-
1989
- 1989-11-28 JP JP1307936A patent/JP2769211B2/en not_active Expired - Lifetime
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9062888B2 (en) | 2008-03-11 | 2015-06-23 | Mitsubishi Electric Corporation | Air conditioner |
| WO2009130954A1 (en) | 2008-04-22 | 2009-10-29 | 三菱電機株式会社 | Blower and heat pump device using same |
| WO2010053037A1 (en) | 2008-11-04 | 2010-05-14 | 三菱電機株式会社 | Blower and heat pump utilizing said blower |
| US9513021B2 (en) | 2008-11-04 | 2016-12-06 | Mitsubishi Electric Corporation | Blower and heat pump apparatus using the same |
| CN102203430B (en) * | 2008-11-04 | 2017-11-10 | 三菱电机株式会社 | Pressure fan and the heat pump assembly using the pressure fan |
| JP2013096622A (en) * | 2011-10-31 | 2013-05-20 | Daikin Industries Ltd | Outdoor unit of air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH03168395A (en) | 1991-07-22 |
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