JPH10196591A - Air conditioner - Google Patents

Air conditioner

Info

Publication number
JPH10196591A
JPH10196591A JP9000053A JP5397A JPH10196591A JP H10196591 A JPH10196591 A JP H10196591A JP 9000053 A JP9000053 A JP 9000053A JP 5397 A JP5397 A JP 5397A JP H10196591 A JPH10196591 A JP H10196591A
Authority
JP
Japan
Prior art keywords
impeller
blade
plate
airflow
side plate
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.)
Pending
Application number
JP9000053A
Other languages
Japanese (ja)
Inventor
Akihiro Yabushita
明弘 藪下
Souzou Suzuki
創三 鈴木
Takumi Kida
琢巳 木田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Holdings Corp
Original Assignee
Matsushita Refrigeration Co
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Matsushita Refrigeration Co filed Critical Matsushita Refrigeration Co
Priority to JP9000053A priority Critical patent/JPH10196591A/en
Publication of JPH10196591A publication Critical patent/JPH10196591A/en
Pending legal-status Critical Current

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  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)

Abstract

PROBLEM TO BE SOLVED: To prevent the break away of the air flow from an upper edge of an impeller on a negative pressure face of the impeller, and the increase of the disorder, and to unify the distribution of an air flow speed at an outlet of the impeller, by inclining the upper edge part of the impeller in a rotating direction of the impeller. SOLUTION: An impeller 10 of a centrifugal blower, comprises plural blades 11, a main plate 12 for fixing the blades 11, and a side plate 13 having an inlet port, and fixed to a side edge face at a side opposite to the main plate, of the blades, and a motor 5 and a heat exchanger 6 are stored and fixed in a easing 7 with the impeller 10. An inlet ring 8 is curved from an inlet edge part 8a to an outlet edge part 8b, and the outlet edge part 8b is inserted into a side plate 13 of the impeller 10. A diameter of the inlet port of the side plate 13, is larger than an inlet diameter of the impeller, and an upper edge part of the impeller 11 is inclined in a rotating direction of the impeller 10. Thereby the inflow air current can be surely attached to the blade negative pressure faces even under the high hydrostatic pressure condition, and the lowering of the blowing performance, and the increase of the turbulent noise can be prevented.

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【０００１】[0001]

【発明の属する技術分野】本発明は、遠心送風機の羽根
車を備えた空気調和機の性能改善に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement in performance of an air conditioner provided with an impeller of a centrifugal blower.

【０００２】[0002]

【従来の技術】近年、遠心送風機の羽根車を備えた空気
調和機は、小形化・高性能化・低騒音化への要求が高ま
り、遠心送風機の羽根車形状や羽根板の断面形状の改良
など、種々の性能向上方法が提案されている。2. Description of the Related Art In recent years, demands for downsizing, high performance, and low noise of an air conditioner having a centrifugal fan impeller have been increased, and the shape of the centrifugal fan impeller and the cross-sectional shape of the impeller have been improved. For example, various performance improvement methods have been proposed.

【０００３】従来の遠心送風機の羽根車を備えた空気調
和機としては、実開平２−６９０９７号公報に示されて
いる。A conventional air conditioner provided with an impeller of a centrifugal blower is disclosed in Japanese Utility Model Laid-Open No. 2-69097.

【０００４】以下、図面を参照しながら、上述した従来
の空気調和機について説明する。図２６は従来の空気調
和機の構造を示す断面図であり、図２７は従来の空気調
和機に搭載された遠心送風機の羽根車の構造を示す断面
図であり、図２８は羽根板の形状を示すＡ−Ａ断面図で
ある。また、図２９は羽根車の回転軸に直交するＢ−Ｂ
断面での羽根断面形状である。Hereinafter, the above-described conventional air conditioner will be described with reference to the drawings. 26 is a cross-sectional view showing the structure of a conventional air conditioner, FIG. 27 is a cross-sectional view showing the structure of an impeller of a centrifugal blower mounted on the conventional air conditioner, and FIG. FIG. FIG. 29 is a cross-sectional view taken along the line BB
It is a blade cross-sectional shape in cross section.

【０００５】図において、１は遠心送風機の羽根車であ
り、複数の羽根板２と羽根板２を固定した円形の主板３
と、羽根板２の反主板側端部に固定した吸込口を有する
側板４とで構成されている。５は羽根車１に直結した電
動機であり、６は羽根車１の吹出側に配設した略環状の
熱交換器であり、羽根車１とともにケーシング７内に収
納、固定されている。８はケーシングに固定された吸込
みリングであり、吸込リング８は入口端部８ａから出口
端部８ｂにかけて湾曲し、その出口端部８ｂは羽根車１
の側板４内に挿入されている。In FIG. 1, reference numeral 1 denotes an impeller of a centrifugal blower, which includes a plurality of blades 2 and a circular main plate 3 to which the blades 2 are fixed.
And a side plate 4 having a suction port fixed to an end of the blade plate 2 on the side opposite to the main plate. Reference numeral 5 denotes an electric motor directly connected to the impeller 1, and reference numeral 6 denotes a substantially annular heat exchanger disposed on the outlet side of the impeller 1, which is housed and fixed together with the impeller 1 in a casing 7. Reference numeral 8 denotes a suction ring fixed to the casing. The suction ring 8 is curved from an inlet end 8a to an outlet end 8b, and the outlet end 8b is connected to the impeller 1.
Is inserted into the side plate 4.

【０００６】また、側板４の吸込み口径Ｄsは羽根板２
の羽根入口径よりＤ1より大きく設定されており、さら
に吸込み口径Ｄsより内径側の羽根板２を羽根車１の回
転軸に対して平行となる平面で切断した断面形状につい
て、羽根板２の回転方向２ａの上端部高さｈ1を反回転
方向面２ｂの上端部高さｈ2より大きくしてある。[0006] In addition, the suction diameter D s of the side plate 4 vanes 2
Vane inlet diameter is set larger than D 1 than, the cross sectional shape taken along a plane to be parallel to the blade plate 2 on the inner diameter side with respect to the axis of rotation of the impeller 1 from the further suction diameter D s, the vane 2 the upper portion height h 1 of the direction of rotation 2a of is made larger than the upper end portion height h 2 of the counter-rotating direction side 2b.

【０００７】さらに、羽根車１の回転軸に直交する羽根
断面において、主板３近傍の羽根断面Ｂ−Ｂから側板４
近傍の羽根断面Ｃ−Ｃまでは図２９に示すように略同一
羽根断面形状としてある。よって、羽根板２の後縁部に
おいて、側板４と羽根板２との結合端部２ｓの位置と主
板３と羽根板２との結合端部２ｈの位置とは図３０に示
すように羽根車１の回転軸に略平行となる位置にある。Further, in the blade section orthogonal to the rotation axis of the impeller 1, the side plate 4
As shown in FIG. 29, the blades have substantially the same blade cross section up to the vicinity blade cross section CC. Therefore, at the trailing edge of the blade 2, the position of the connection end 2 s between the side plate 4 and the blade 2 and the position of the connection end 2 h between the main plate 3 and the blade 2 are as shown in FIG. 30. It is located at a position substantially parallel to one rotation axis.

【０００８】以上のように構成された空気調和機につい
て以下その動作を説明する。まず、電動機５の駆動力に
よって羽根車１が所定の回転方向に回転すると、空気が
吸込みリング８を介して羽根車１内に流入され、複数の
羽根板２の間を通過する際に静圧と動圧を付加され、さ
らに、熱交換器６を通過する際に加熱または冷却され、
吹出口９より吹き出されて、室内温度と室内湿度を調節
する作用を為す。The operation of the air conditioner configured as described above will be described below. First, when the impeller 1 rotates in a predetermined rotation direction by the driving force of the electric motor 5, air flows into the impeller 1 through the suction ring 8, and when passing between the plurality of impellers 2, a static pressure is applied. And a dynamic pressure, and further heated or cooled when passing through the heat exchanger 6,
The air is blown out from the air outlet 9 and functions to adjust the indoor temperature and the indoor humidity.

【０００９】このとき、側板４の吸込み口径Ｄsは羽根
入口径Ｄ1より大きく設定されているため、吸込み口面
積が大きくなり吸込み気流の速度が低くなる。よって、
羽根車１への流入抵抗および羽根車１内部での流動抵抗
（損失）が小さくなり、圧力の低い動作点では風量が増
加し送風性能が向上する。[0009] At this time, the suction diameter D s of the side plate 4 because it is larger than the vane inlet diameter D 1, the speed of the suction inlet area increases airflow decreases. Therefore,
The flow resistance (loss) into the impeller 1 and the flow resistance (loss) inside the impeller 1 are reduced, and the air volume is increased at the operating point where the pressure is low, so that the blowing performance is improved.

【００１０】また、吸込み口径Ｄsより内径側の羽根板
２を羽根車１の回転軸に対して平行となる平面で切断し
た断面状では、羽根板２の回転方向面２ａの上端部高さ
ｈ1を反回転方向面２ｂの上端部高さｈ2より大きくして
あるため、羽根板２の上端部では、図２８に示す流入気
流Ｏに対して羽根板２の負圧面側に迎え角が設定された
ことになり、羽根板２の上端部より流入する気流Ｏは羽
根板２の上端部で一端羽根板２の負圧面に付着し、その
後、羽根板２に沿って流れるため、羽根板２の上端部に
おける気流の剥離を抑制する。[0010] In the cross-sectional shape taken along a plane to be parallel to the blade plate 2 on the inner diameter side with respect to the axis of rotation of the impeller 1 from the suction diameter D s, the upper end height of the rotational direction surface 2a of the vane 2 since the h 1 is made larger than the upper end portion height h 2 of the counter-rotating direction side 2b, the upper end portion of the vane 2, the angle of attack on the suction side of the vane 2 against the incoming air flow O shown in FIG. 28 Is set, and the airflow O flowing from the upper end of the blade plate 2 adheres to the negative pressure surface of the blade plate 2 at one end at the upper end of the blade plate 2 and thereafter flows along the blade plate 2. The separation of the airflow at the upper end of the plate 2 is suppressed.

【００１１】[0011]

【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、羽根板２の上端部における気流剥離防
止効果は羽根２上端部負圧面の傾斜形状によって発生す
るため、その効果量は板厚に依存するが、板厚を厚くす
ると羽根車１内部の気流通過面積が減少し、羽根車１の
送風性能を劣化させるため一定以上の厚さにすることは
できず、従って、羽根負圧面への気流付着効果は特定の
動作点条件のごく近傍の流入気流に対して得られるのみ
であり、動作点が設計点より高静圧条件に変化した場合
には、羽根板２の上端部からの流入気流が羽根板２の上
端の負圧面２ｂに付着せず剥離し、送風性能の低下およ
び乱流騒音の増加原因となる。However, in the above configuration, the effect of preventing air flow separation at the upper end portion of the blade plate 2 is generated by the inclined shape of the negative pressure surface at the upper end portion of the blade plate 2. However, if the plate thickness is increased, the air flow passage area inside the impeller 1 decreases, and the air blowing performance of the impeller 1 is deteriorated. Is only obtained for an inflow airflow very close to a specific operating point condition, and when the operating point changes from the design point to a higher static pressure condition, the airflow from the upper end of the blade plate 2 The inflow airflow separates without adhering to the negative pressure surface 2b at the upper end of the blade plate 2, which causes a reduction in air blowing performance and an increase in turbulent noise.

【００１２】またさらに、空気調和機は小型コンパクト
化が要求される中、ケーシング７の大きさを小さくする
ため、略環状の熱交換器６の径を小さく設定される。そ
こで、伝熱性能低下分を補うため、熱交換器６の高さを
高くする手法がとられ、それに、伴い、羽根車１の軸方
向長さを大きくすることにより、熱交換器６を通過する
気流速度分布を改善することがされている。Further, in the case where the size and size of the air conditioner are required, the diameter of the substantially annular heat exchanger 6 is set small in order to reduce the size of the casing 7. Therefore, in order to compensate for the decrease in the heat transfer performance, a method of increasing the height of the heat exchanger 6 has been adopted, and accordingly, the axial length of the impeller 1 has been increased to allow the impeller 1 to pass through the heat exchanger 6. Airflow velocity distribution has been improved.

【００１３】ところが、羽根車１内に流入した気流の方
向は、側板４の吸込口における軸方向の流れから羽根板
２間の流入する際に半径方向の流れへと曲がるため、側
板４に近いほど気流の曲率が大きくなり流速が低下す
る。しかし、主板３近傍の羽根板２の羽根断面形状と側
板４近傍の羽根板２の羽根断面形状は同等であるため、
羽根板が気流に与える作用も同等となる。However, the direction of the air flow that has flowed into the impeller 1 is closer to the side plate 4 because the flow is bent from the axial flow at the suction port of the side plate 4 to the radial flow when flowing between the blade plates 2. As the curvature of the air flow increases, the flow velocity decreases. However, since the cross-sectional shape of the blade 2 near the main plate 3 is the same as the cross-sectional shape of the blade 2 near the side plate 4,
The action of the blades on the airflow is equivalent.

【００１４】従って、側板４の近傍では羽根板２に流入
する気流の速度が低いために羽根板２の出口における気
流速度も低くなり、図３１に示すように羽根車１出口に
おける気流速度分布は、側板４側での流速が主板３側の
流速にくらべ大幅に低下する。この傾向は羽根車１の軸
方向長さを大きくするほど顕著となるが、そのため、熱
交換器６の熱交換量が低下するとともに、遠心送風機の
送風性能および送風効率を低下させ、速板４近傍の気流
の剥離と乱れを引き起こし乱入騒音を増加させるという
課題を有していた。Therefore, near the side plate 4, the velocity of the airflow flowing into the impeller 2 is low, so that the airflow velocity at the exit of the impeller 2 is also low. As shown in FIG. In addition, the flow velocity on the side plate 4 side is significantly lower than the flow velocity on the main plate 3 side. This tendency becomes more remarkable as the axial length of the impeller 1 is increased. Therefore, the amount of heat exchange of the heat exchanger 6 is reduced, and the blowing performance and the blowing efficiency of the centrifugal blower are reduced. There was a problem of causing separation and turbulence of the nearby airflow to increase turbulent noise.

【００１５】本発明は上記課題を鑑み、高静圧条件下で
使用される場合でも、羽根板の上端部から流入する気流
が羽根板負圧面で剥離することと乱れが増加することを
抑制し、さらに、側板側の気流速度を増速して羽根車出
口における気流速度分布を均一化することにより、送風
性能を改善して、乱流騒音を低減し、さらに、熱交換器
の熱交換量が低下するのを防止することができる空気調
和機を提供するものである。In view of the above problems, the present invention suppresses the separation of the airflow flowing from the upper end of the blade plate on the blade negative pressure surface and the increase in turbulence even when used under high static pressure conditions. Further, by increasing the airflow velocity on the side plate side to make the airflow velocity distribution at the impeller outlet uniform, the blowing performance is improved, the turbulent noise is reduced, and the heat exchange amount of the heat exchanger is further increased. It is an object of the present invention to provide an air conditioner that can prevent the air conditioner from decreasing.

【００１６】[0016]

【課題を解決するための手段】この課題を解決するため
に本発明は、遠心送風機が設計動作点より高静圧条件下
で使用される場合でも、羽根板の板厚を厚くすることな
く、羽根板の上端部からの流入気流が羽根負圧面に付着
し、羽根板に沿って流れるように構成したものである。In order to solve this problem, the present invention provides a centrifugal blower which does not increase the thickness of the blades even when the centrifugal blower is used under conditions of higher static pressure than a design operating point. The inflow airflow from the upper end of the blade plate adheres to the blade negative pressure surface, and flows along the blade plate.

【００１７】これにより、高静圧条件下て使用される場
合でも、羽根上端部からの流入気流を確実に羽根負圧面
に付着させ、送風性能の低下および乱流騒音の増加を抑
えることができる。Thus, even when used under high static pressure conditions, the inflow airflow from the upper end portion of the blade can be reliably adhered to the blade negative pressure surface, thereby suppressing a reduction in air blowing performance and an increase in turbulent noise. .

【００１８】[0018]

【発明の実施の形態】請求項１記載の発明は、複数の羽
根板と、前記羽根板を固定した主板と、前記羽根板の反
主板側端面に固定した吸込口を有する側板とで形成して
なる遠心送風機の羽根車と、前記側板の吸込口に挿入し
た吸込リングと、前記羽根車の吹出側に配設した略環状
の熱交換器と、前記羽根車と前記吸込リングと前記熱交
換器とを内部におさめたケーシングで構成された空気調
和機において、前記羽根板の上端部を前記羽根車の回転
方向に傾斜させたので、羽根板厚を厚くすることなく羽
根上端部負圧面の傾斜を大きくすることになる。そのた
め、遠心送風機が設計動作点より高静圧条件下で使用さ
れる場合でも、羽根板の上端部からの流入気流が羽根負
圧面に付着し、羽根板に沿って流れる。よって、羽根上
端部からの流入気流を羽根負圧面に付着させ、送風性能
の低下および乱流騒音の増加を抑えることができる。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The invention according to claim 1 comprises a plurality of blades, a main plate to which the blades are fixed, and a side plate having a suction port fixed to an end face of the blades on the side opposite to the main plate. A centrifugal blower, a suction ring inserted into a suction port of the side plate, a substantially annular heat exchanger disposed on an outlet side of the impeller, and the heat exchange between the impeller and the suction ring. In the air conditioner composed of a casing having a container inside, the upper end of the blade plate is inclined in the rotation direction of the impeller, so that the upper end portion of the blade upper surface negative pressure surface is not thickened. This will increase the slope. Therefore, even when the centrifugal blower is used under conditions of higher static pressure than the design operating point, the inflow airflow from the upper end of the blade plate adheres to the blade negative pressure surface and flows along the blade plate. Therefore, the inflow airflow from the upper end portion of the blade is made to adhere to the blade negative pressure surface, so that it is possible to suppress a decrease in the blowing performance and an increase in turbulent noise.

【００１９】請求項２記載の発明は、請求項１記載の発
明からさらに、羽根車の回転軸に直交する羽根断面にお
いて、側板近傍羽根断面の羽根出口角を主板近傍断面の
羽根出口角より大きく設定し、前記主板から前記側板ま
での羽根断面形状を連続的に変化させたので、側板側の
羽根板の仕事量を主板側の羽根仕事量より増加させて側
板側の流速を増加させ羽根車出口における気流速度分布
を均一化することになる。そのため、送風性能を改善
し、側板近傍の気流の剥離と乱れを抑制することにより
乱流騒音を低減し、さらに、熱交換器の熱交換量が低下
するのを防止することができる。According to a second aspect of the present invention, in the blade section perpendicular to the rotation axis of the impeller, the blade exit angle in the section near the side plate is larger than the blade exit angle in the section near the main plate. Since the blade cross-sectional shape from the main plate to the side plate was continuously changed, the work amount of the side plate-side blade plate was increased from the work amount of the main plate-side blade to increase the flow speed on the side plate side, and The airflow velocity distribution at the outlet will be made uniform. Therefore, it is possible to improve the air blowing performance, reduce the turbulence noise by suppressing the separation and turbulence of the air flow near the side plate, and prevent the heat exchange amount of the heat exchanger from being reduced.

【００２０】また、遠心送風機の羽根車が設計動作点よ
り高静圧条件下で使用される場合、羽根車を通過する空
気の流量が減少して、羽根車へ流入する気流の速度が小
さくなるため、側板の吸込口を流れる流入気流に対して
働く力の作用は、軸方向成分が減少し、羽根板の吸引力
により発生する半径方向成分が大きくなった結果、側板
の吸込口において羽根車内に流入しようとする気流は、
既に羽根車の出口方向に傾いた流れとなる。Further, when the impeller of the centrifugal blower is used under a higher static pressure condition than the design operating point, the flow rate of the air passing through the impeller decreases, and the speed of the airflow flowing into the impeller decreases. Therefore, the effect of the force acting on the inflow airflow flowing through the suction port of the side plate is such that the axial component is reduced and the radial component generated by the suction force of the blade plate is increased. The airflow that is going to flow into
The flow is already inclined toward the exit of the impeller.

【００２１】よって、側板側と主板側との気流の曲率差
が小さくなり、側板の近傍では羽根板に流入する気流の
速度が大きくなるため、羽根車の出口における気流速度
が側板側で逆に大きくなうとするが、上端部を羽根車の
回転方向に傾斜させた羽根板に導かれ羽根負圧面および
羽根加圧面に付着した気流は、主板側へと流れるため、
側板側での吹出気流速度が大きくなりすぎるのを抑制す
る効果が得られる。Therefore, the difference in the curvature of the airflow between the side plate and the main plate is reduced, and the speed of the airflow flowing into the impeller near the side plate is increased. Therefore, the airflow velocity at the outlet of the impeller is reversed on the side plate side. Although it tends to increase, the airflow that is guided to the blade plate whose upper end is inclined in the rotation direction of the impeller and adheres to the blade negative pressure surface and the blade pressing surface flows to the main plate side,
The effect of suppressing the blowout airflow velocity on the side plate side from becoming too large can be obtained.

【００２２】さらにまた、遠心送風機の羽根車が設計動
作点より高静圧条件下で使用される場合、側板近傍羽根
断面の羽根出口角を大きく設定したことにより、側板側
の羽根負圧面にて気流の剥離が発生し、乱れが増加しよ
うとするが、上端部を羽根車の回転方向に傾斜させた羽
根板に導かれ羽根負圧面に付着した気流は、側板側の羽
根負圧面部を流れるため、気流が剥離しようとするのを
抑制する効果が得られる。Further, when the impeller of the centrifugal blower is used under high static pressure conditions from the design operating point, the blade exit angle of the blade section near the side plate is set to be large, so that the blade negative pressure surface on the side plate side is set. Airflow separation occurs and turbulence tends to increase, but the airflow guided to the blade plate whose upper end is inclined in the direction of rotation of the impeller and adhered to the blade negative pressure surface flows through the blade negative pressure surface portion on the side plate side. Therefore, an effect of suppressing the air flow from separating is obtained.

【００２３】請求項３記載の発明は、請求項１記載の発
明からさらに、羽根板の後縁部において、側板と前記羽
根板との結合端部の位置を主板と前記羽根板との結合端
部の位置より回転方向とは逆向きの位置に設定し、前記
主板から前記側板までの前記羽根板の後縁部を連続的に
変化させたので、羽根板を通過する気流に対して働く力
の作用は、回転軸に垂直な平面内の成分のみでなく、主
板側から側板側へ向かう成分も生じるため、気流が側板
側に偏り、側板側の流速を増加させ羽根車出口における
気流速度分布を均一化することになる。そのため、送風
性能を改善し、側板近傍の気流の剥離と乱れを抑制する
ことにより乱流騒音を低減し、さらに、熱交換器の熱交
換量が低下するのを防止することができる。According to a third aspect of the present invention, in addition to the first aspect of the present invention, the position of the connection end between the side plate and the blade plate at the rear edge of the blade plate is changed to the connection end between the main plate and the blade plate. The position of the blade is set to a position opposite to the direction of rotation from the position of the part, and the rear edge of the blade from the main plate to the side plate is continuously changed, so that the force acting on the airflow passing through the blade The effect of this is that not only components in a plane perpendicular to the rotation axis, but also components from the main plate side to the side plate side are generated, the air flow is biased to the side plate side, the flow velocity on the side plate side is increased, and the air flow velocity distribution at the impeller outlet Will be uniformed. Therefore, it is possible to improve the air blowing performance, reduce the turbulence noise by suppressing the separation and turbulence of the air flow near the side plate, and prevent the heat exchange amount of the heat exchanger from being reduced.

【００２４】また、遠心送風機の羽根車が設計動作点よ
り高静圧条件下で使用される場合、羽根車を通過する空
気の流量が減少して、羽根車へ流入する気流の速度が小
さくなるため、側板の吸込口を流れる流入気流に対して
働く力の作用は、軸方向成分が減少し、羽根板の吸引力
により発生する半径方向成分が大きくなった結果、側板
の吸込口において羽根車内に流入しようとする気流は、
既に羽根車の出口方向に傾いた流れとなる。When the impeller of the centrifugal blower is used under a condition of higher static pressure than the design operating point, the flow rate of the air passing through the impeller decreases, and the speed of the airflow flowing into the impeller decreases. Therefore, the effect of the force acting on the inflow airflow flowing through the suction port of the side plate is such that the axial component is reduced and the radial component generated by the suction force of the blade plate is increased. The airflow that is going to flow into
The flow is already inclined toward the exit of the impeller.

【００２５】よって、側板側と主板側との気流の曲率差
が小さくなり、側板の近傍では羽根板に流入する気流の
速度が大きくなるため、羽根車の出口における気流速度
が側板側で逆に大きくなろうとするが、上端部を羽根車
の回転方向に傾斜させた羽根板に導かれ羽根負圧面およ
び羽根加圧面に付着した気流は、主板側へと流れるた
め、側板側での吹出気流速度が大きくなりすぎるのを抑
制する効果が得られる。Therefore, the difference in the curvature of the airflow between the side plate side and the main plate side becomes small, and the speed of the airflow flowing into the blade plate near the side plate becomes large, so that the airflow speed at the outlet of the impeller is reversed on the side plate side. However, the airflow adhering to the blade negative pressure surface and the blade pressing surface, which is guided to the blade plate whose upper end is inclined in the rotation direction of the impeller, flows to the main plate side, so that the blowing air velocity at the side plate side Is suppressed.

【００２６】さらにまた、羽根板の後縁部において、側
板と羽根板との結合端部の位置を主板と羽根板との結合
端部の位置より回転方向とは逆向きの位置に設定するた
め、羽根車の回転軸に直交する各羽根断面において、各
羽根入口断面を主板近傍の羽根入口断面に内包させ、側
板近傍羽根断面の羽根出口角を主板近傍羽根断面の羽根
出口角より小さくする場合がある。Furthermore, at the rear edge of the blade plate, the position of the joint end between the side plate and the blade plate is set at a position opposite to the rotational direction from the position of the joint end between the main plate and the blade plate. In the case of each blade section orthogonal to the rotation axis of the impeller, each blade inlet section is included in the blade inlet section near the main plate, and the blade outlet angle of the blade section near the side plate is smaller than the blade outlet angle of the blade section near the main plate. There is.

【００２７】この場合、遠心送風機の羽根車が設計動作
点より高静圧条件下での使用となった時、主板近傍羽根
断面の羽根出口角を大きく設定したことにより、主板側
の羽根負圧面にて気流の剥離が発生し、乱れが増加しよ
うとするが、上端部を羽根車の回転方向に傾斜させた羽
根板に導かれ羽根負圧面に付着した気流は、主板側の羽
根負圧面部まで流れるため、気流が剥離しようとするの
を抑制する効果が得られる。In this case, when the impeller of the centrifugal blower is used under high static pressure conditions from the design operating point, the blade exit angle of the blade section near the main plate is set to be large, so that the blade negative pressure surface on the main plate side is set. Airflow separation occurs and turbulence tends to increase, but the airflow guided to the blade plate whose upper end is inclined in the rotation direction of the impeller and adhered to the blade negative pressure surface is a blade negative pressure surface portion on the main plate side. Therefore, an effect of suppressing the airflow from separating is obtained.

【００２８】[0028]

【実施例】【Example】

（実施例１）図１は本発明の実施例１における空気調和
機の構造を、図２は図１の同実施例１における空気調和
機に搭載した遠心送風機の羽根車の斜視図を、また、図
３は図１の同実施例１における遠心送風機の羽根車の構
造を、さらに、図４は図１の同実施例１における遠心送
風機の羽根車のＤ−Ｄ断面を示すものである。(Embodiment 1) FIG. 1 shows a structure of an air conditioner in Embodiment 1 of the present invention, FIG. 2 is a perspective view of an impeller of a centrifugal blower mounted on the air conditioner in Embodiment 1 of FIG. 3 shows the structure of the impeller of the centrifugal blower according to the first embodiment shown in FIG. 1, and FIG. 4 shows a cross section taken along line D-D of the impeller of the centrifugal blower according to the first embodiment shown in FIG.

【００２９】図において、１０は遠心送風機の羽根車で
あり、複数の羽根板１１と羽根板１１を固定した主板１
２と、羽根板１１の反主板側端面に固定した吸込口を有
する側板１３とで構成されている。５は羽根車１０に直
結した電動機であり、６は羽根車１０の吹出側に配設し
た略環状の熱交換器であり、羽根車１０とともにケーシ
ング７内に収納、固定されている。８はケーシングに固
定された吸込みリングであり、吸込リング８は入口端部
８ａから出口端部８ｂにかけて湾曲し、その出口端部８
ｂは羽根車１０の側板１３内に挿入されている。In the figure, reference numeral 10 denotes an impeller of a centrifugal blower, and a plurality of blade plates 11 and a main plate 1 to which the blade plates 11 are fixed.
2 and a side plate 13 having a suction port fixed to the end surface of the blade plate 11 on the side opposite to the main plate. Reference numeral 5 denotes an electric motor directly connected to the impeller 10, and reference numeral 6 denotes a substantially annular heat exchanger disposed on the outlet side of the impeller 10, which is housed and fixed together with the impeller 10 in a casing 7. Reference numeral 8 denotes a suction ring fixed to the casing. The suction ring 8 is curved from an inlet end 8a to an outlet end 8b, and has an outlet end 8b.
b is inserted into the side plate 13 of the impeller 10.

【００３０】また、側板１１の吸込み口径Ｄsは羽根入
口径Ｄ1より大きく設定されており、さらにまた、羽根
板１１の上端部を羽根車１０の回転方向に傾斜させてい
る。The suction diameter D s of the side plate 11 is set to be larger than the blade entrance diameter D 1 , and the upper end of the blade plate 11 is inclined in the rotation direction of the impeller 10.

【００３１】以上のように構成された遠心送風機につい
て以下その動作を説明する。まず、電動機５の駆動力に
よって羽根車１０が所定の回転方向に回転すると、空気
が吸込みリング８を介して羽根車１０内に流入され、複
数の羽根板１１の間を通過する際に静圧と動圧を付加さ
れ、さらに、熱交換器６を通過する際に加熱または冷却
され、吹出口９より吹き出されて、室内温度と室内湿度
を調整する作用を為す。The operation of the centrifugal blower constructed as described above will be described below. First, when the impeller 10 rotates in a predetermined rotation direction by the driving force of the electric motor 5, air flows into the impeller 10 via the suction ring 8, and a static pressure is generated when passing between the plurality of blade plates 11. Further, it is heated or cooled when passing through the heat exchanger 6 and is blown out from the blow-out port 9 to adjust the room temperature and the room humidity.

【００３２】このとき、遠心送風機の騒音レベルは図５
に示すように、羽根板１１の最小羽根入口径Ｄ1と羽根
車１０の外径Ｄ2によって変化するが、最小羽根入口径
Ｄ1を０．６５Ｄ2≦Ｄ1≦０．８Ｄ2とすることにより、
ほぼ適正化することができ、低騒音な羽根車を構成する
ことができる。At this time, the noise level of the centrifugal blower is as shown in FIG.
As shown in, varies by the outer diameter D 2 of the minimum blade inlet diameter D 1 and the impeller 10 of the slats 11, the minimum blade inlet diameter D 1 and 0.65D 2 ≦ D 1 ≦ 0.8D 2 By doing
It can be made almost appropriate, and a low-noise impeller can be configured.

【００３３】なお、最小羽根入口径Ｄ1を０．７Ｄ2≦Ｄ
1≦０．７５Ｄ2とすることにより、ほほ適正化すること
ができ、さらに低騒音な羽根車を構成することができ
る。The minimum blade inlet diameter D 1 is set to 0.7D 2 ≦ D
By setting 1 ≦ 0.75D 2 , it is possible to make it more appropriate and to configure an impeller with lower noise.

【００３４】また、羽根板１１の側板１３における側端
部１３ａでの羽根入口径Ｄtを側板１３の吸込み口径Ｄs
より大きくすることにより、流入気流が羽根上端部から
流入することになり、吸込み口面積が大きいため吸込み
気流の速度が低くなり、羽根車１０への流入抵抗および
羽根車１０内部での流動抵抗（損失）が小さくなり、圧
力の低い動作点では風量が送風性能を向上することがで
きる。Further, the suction vane inlet diameter D t of the side edge portion 13a of the side plate 13 of the slats 11 of the side plate 13 diameter D s
By making it larger, the inflow airflow flows in from the upper end of the blade, the speed of the suction airflow decreases due to the large suction opening area, and the inflow resistance to the impeller 10 and the flow resistance inside the impeller 10 ( Loss) is small, and the air volume can improve the blowing performance at the operating point where the pressure is low.

【００３５】ここで、羽根板１１の上端部を羽根車１０
の回転方向に傾斜させているので、羽根板１０の上端部
が流入気流Ｐを偏向させ、羽根板１１の上端部を傾斜さ
せた部分の羽根負圧面１１ａに気流を導き、さらに下流
側の羽根板１１の略垂直部分の羽根負圧面１１ｂに安定
した気流を案内するため、羽根板１１の羽根負圧面での
気流の剃離を抑制する。Here, the upper end of the blade plate 11 is
, The upper end of the blade plate 10 deflects the inflow airflow P and guides the airflow to the blade negative pressure surface 11 a where the upper end of the blade plate 11 is inclined. In order to guide a stable airflow to the blade negative pressure surface 11b of the substantially vertical portion of the plate 11, shaving of the airflow on the blade negative pressure surface of the blade plate 11 is suppressed.

【００３６】従って、羽根車１０が設計動作点より高静
圧条件下で使用される場合でも、羽根板１１の上端部か
らの流入気流Ｐが羽根負圧面に付着し、羽根板１１に沿
って流れる。よって、羽根板１１の上端部からの流入気
流を羽根負圧面に付着させ、送風性能の低下および乱流
騒音の増加を抑えることができる。Therefore, even when the impeller 10 is used under a condition of higher static pressure than the design operating point, the inflow airflow P from the upper end of the blade plate 11 adheres to the blade negative pressure surface and follows the blade plate 11. Flows. Therefore, the inflow airflow from the upper end portion of the blade plate 11 is made to adhere to the blade negative pressure surface, so that a decrease in the blowing performance and an increase in turbulent noise can be suppressed.

【００３７】以上のように本実施例によれば、羽根板１
１の上端部を羽根車１０の回転方向に傾斜させることに
より、羽根板１１の上端部が流入気流Ｐを偏向させ、羽
根板１１の上端部を傾斜させた部分の羽根負圧面１１ａ
に気流を導き、さらに下流側の羽根板１１の垂直部分の
羽根負圧面１１ｂに安定した気流を案内するため、羽根
負圧面での気流の剃離を抑制することができ、羽根車１
０の設計動作点より高静圧な動作点で作動する場合でも
送風能力の低下を抑制すると共に、流れの剃離に伴う乱
流騒音の増加を抑えることができる。As described above, according to the present embodiment, the blade 1
1 is inclined in the rotation direction of the impeller 10, so that the upper end of the blade plate 11 deflects the inflow airflow P, and the blade negative pressure surface 11a of the portion where the upper end of the blade plate 11 is inclined.
In order to guide the air flow to the blade negative pressure surface 11b in the vertical portion of the blade plate 11 on the downstream side, it is possible to suppress the separation of the air flow on the blade negative pressure surface, and
Even when operating at an operating point with a higher static pressure than the design operating point of 0, it is possible to suppress a decrease in the blowing capacity and to suppress an increase in turbulent noise due to separation of the flow.

【００３８】（実施例２）図６は本発明の実施例２にお
ける空気調和機に搭載した遠心送風機の羽根車の構造
を、図７は図６の同実施例２における遠心送風機の羽根
車の斜視図を、また、図８、９、１０はそれぞれ図６の
同実施例２における遠心送風機の羽根車のＥ−Ｅ断面、
Ｆ−Ｆ断面、Ｇ−Ｇ断面を示すものである。(Embodiment 2) FIG. 6 shows the structure of an impeller of a centrifugal blower mounted on an air conditioner in Embodiment 2 of the present invention, and FIG. 7 shows the structure of the impeller of the centrifugal blower in Embodiment 2 of FIG. 8, 9, and 10 are cross-sectional views of the impeller of the centrifugal blower according to the second embodiment shown in FIG.
It shows an FF section and a GG section.

【００３９】図において、本発明の実施例１における空
気調和機からさらに、羽根車１４の回転軸に直交する羽
根板１５の断面において、側板１６近傍羽根断面の羽根
出口角βｓを主板１７近傍羽根断面の羽根出口角βｈよ
り大きく設定し、主板１７から側板１６までの羽根断面
形状を連続的に変化させている。In the drawing, the blade outlet angle βs of the cross section of the blade near the side plate 16 is further changed from the blade near the main plate 17 in the cross section of the blade 15 orthogonal to the rotation axis of the impeller 14 from the air conditioner according to the first embodiment of the present invention. The blade exit angle βh of the cross section is set to be larger, and the blade cross section from the main plate 17 to the side plate 16 is continuously changed.

【００４０】以上のように構成された空気調和機につい
て以下その動作を説明する。まず、電動機５の駆動力に
よって羽根車１４が所定の回転方向に回転すると、空気
が吸込みリング８を介して羽根車１４内に流入され、複
数の羽根板１５の間を通過する際に静圧と動圧を付加さ
れ、さらに、熱交換器６を通過する際に加熱または冷却
され、吹出口９より吹き出されて、室内温度と室内湿度
を調節する作用を為す。The operation of the air conditioner configured as described above will be described below. First, when the impeller 14 rotates in a predetermined rotation direction by the driving force of the electric motor 5, air flows into the impeller 14 via the suction ring 8 and generates static pressure when passing between the plurality of blades 15. Further, it is heated or cooled when passing through the heat exchanger 6, and is blown out from the blow-out port 9 to adjust the room temperature and the room humidity.

【００４１】ここで、羽根車１４の回転軸に直交する羽
根断面において、側板１６近傍羽根断面の羽根出口角β
ｓを主板１７近傍羽根断面の羽根出口角βｈより大きく
設定し、主板１７から側板１６までの羽根断面形状を連
続的に変化させたので、側板１６側の羽根板１５の仕事
量を主板１７側の羽根仕事量より増加させて側板１５側
の流速を増加させ、図１１に示すように羽根車１４の出
口における気流速度分布を均一化することになる。Here, in the blade section orthogonal to the rotation axis of the impeller 14, the blade exit angle β of the blade section near the side plate 16
Since s is set to be larger than the blade exit angle βh of the blade section near the main plate 17 and the blade cross section from the main plate 17 to the side plate 16 is continuously changed, the work amount of the blade plate 15 on the side plate 16 side is reduced. 11 to increase the flow velocity on the side plate 15 side, thereby making the air flow velocity distribution at the exit of the impeller 14 uniform as shown in FIG.

【００４２】そのため、送風性能を改善し、側板１６近
傍の気流の剃離と乱れを抑制することにより乱流騒音を
低減し、さらに、熱交換器６の熱交換量が低下するのを
防止することができる。For this reason, the air blowing performance is improved, the turbulence noise is reduced by suppressing the separation and turbulence of the air flow near the side plate 16, and the heat exchange amount of the heat exchanger 6 is prevented from being reduced. be able to.

【００４３】また、遠心送風機の羽根車１４が設計動作
点より高静圧条件下で使用される場合、羽根車１４を通
過する空気の流量が減少して、羽根車１４へ流入する気
流の速度が小さくなるため、側板１６の吸込口を流れる
流入気流に対して働く力の作用は、軸方向成分が減少
し、羽根板１５の吸引力により発生する半径方向成分が
大きくなった結果、側板１６の吸込口において羽根車１
４内に流入しようとする気流は、既に羽根車１４の出口
方向に傾いた流れとなる。When the impeller 14 of the centrifugal blower is used under conditions of higher static pressure than the design operating point, the flow rate of air passing through the impeller 14 decreases, and the speed of the airflow flowing into the impeller 14 decreases. Is reduced, the axial component of the force acting on the inflow airflow flowing through the suction port of the side plate 16 decreases, and the radial component generated by the suction force of the blade plate 15 increases. Impeller 1 at the suction port
The airflow that is going to flow into the inside 4 is already inclined toward the exit of the impeller 14.

【００４４】よって、側板１６側と主板１７側との気流
の曲率差が小さくなり、側板１６の近傍では羽根板１５
に流入する気流の速度が大きくなるため、羽根車１４の
出口における気流速度が側板１６側で逆に大きくなろう
とするが、上端部を羽根車１４の回転方向に傾斜させた
羽根板１５に導かれ羽根負圧面１５ａおよび羽根加圧面
１５ｂに付着した気流Ｑは、主板側１７へと流れるた
め、側板１６側での吹出気流速度が大きくなりすぎるの
を抑制する効果が得られる。Accordingly, the difference in the curvature of the airflow between the side plate 16 and the main plate 17 is reduced, and the blade plate 15 is provided near the side plate 16.
Since the speed of the airflow flowing into the impeller increases, the airflow speed at the exit of the impeller 14 tends to increase on the side plate 16 side, but the upper end is guided to the impeller 15 inclined in the rotation direction of the impeller 14. Since the airflow Q attached to the blade negative pressure surface 15a and the blade pressing surface 15b flows to the main plate side 17, an effect of suppressing an excessive increase in the blown airflow velocity on the side plate 16 side can be obtained.

【００４５】さらにまた、遠心送風機の羽根車１４が設
計動作点より高静圧条件下で使用される場合、側板１６
近傍羽根断面の羽根手口角βｓを大きく設定したことに
より、側板１６側の羽根負圧面にて気流の剃離が発生
し、乱れが増加しようとするが、上端部を羽根車１４の
回転方向に傾斜させた羽根板１５に導かれ羽根負圧面１
５ａに付着した気流Ｑは、側板１６側の羽根負圧面部を
流れるため、気流剃離しようとするのを抑制する効果が
得られる。Further, when the impeller 14 of the centrifugal blower is used under conditions of higher static pressure than the design operating point, the side plate 16
By setting the blade hand opening angle βs of the vicinity blade cross section to be large, airflow shaving occurs on the blade negative pressure surface on the side plate 16 side, and turbulence tends to increase, but the upper end portion is moved in the rotation direction of the impeller 14. The blade negative pressure surface 1 guided to the inclined blade plate 15
Since the airflow Q adhering to 5a flows through the blade negative pressure surface portion on the side plate 16 side, an effect of suppressing an attempt to separate the airflow can be obtained.

【００４６】従って、羽根車１４が設計動作点より高静
圧条件下で使用される場合でも、羽根板１５の上端部か
らの流入気流Ｑが羽根負圧面に付着し、羽根板１５に沿
って流れ、羽根板１５の上端部からの流入気流を羽根負
圧面に付着させ、さらに、側板１６側の羽根板１５の仕
事量を主板１７側の羽根仕事量より増加させて側板１５
側の流速を増加させ羽根車１４の出口における気流速度
分布を均一化することができる。Therefore, even when the impeller 14 is used under a condition of higher static pressure than the design operating point, the inflow airflow Q from the upper end of the blade plate 15 adheres to the blade negative pressure surface and follows the blade plate 15. The flow and the inflow airflow from the upper end of the blade plate 15 adhere to the blade negative pressure surface, and the work of the blade plate 15 on the side plate 16 side is increased from the work amount of the blade on the main plate 17 side.
By increasing the flow velocity on the side, the airflow velocity distribution at the outlet of the impeller 14 can be made uniform.

【００４７】そのため、送風性能を改善し、側板１６近
傍の気流の剃離と乱れを抑制することにより乱流騒音を
低減し、さらに、熱交換器６の熱交換量が低下するのを
防止することができる。For this reason, the air blowing performance is improved, the turbulence noise is reduced by suppressing the shaving and turbulence of the air flow near the side plate 16, and the heat exchange amount of the heat exchanger 6 is prevented from being reduced. be able to.

【００４８】以上のように本実施例によれば、羽根車１
４の回転軸に直交する羽根断面において、側板１６近傍
羽根断面の羽根出口角βｓを主板１７近傍羽根断面の羽
根出口角βｈより大きく設定し、主板１７から側板１６
までの羽根断面形状を連続的に変化させることにより、
羽根車１４が設計動作点より高静圧条件下で使用される
場合でも、羽根板１５の上端部からの流入気流Ｑが羽根
負圧面に付着し、さらに、側板１６側の羽根板１５の仕
事量を主板１７側の羽根仕事量より増加させて、羽根車
１４の出口における気流速度分布を均一化することがで
きるため、送風性能を改善し、側板１６近傍の気流の剃
離と乱れを抑制することにより乱流騒音を低減し、さら
に、熱交換器６の熱交換量が低下するのを防止すること
ができる。As described above, according to the present embodiment, the impeller 1
4, the blade outlet angle βs of the blade cross section near the side plate 16 is set to be larger than the blade outlet angle βh of the blade cross section near the main plate 17,
By continuously changing the blade cross-sectional shape up to
Even when the impeller 14 is used under higher static pressure conditions than the design operating point, the inflow airflow Q from the upper end of the blade plate 15 adheres to the blade negative pressure surface, and furthermore, the work of the blade plate 15 on the side plate 16 side. Since the air flow rate at the exit of the impeller 14 can be made uniform by increasing the amount of work from the blade work amount on the main plate 17 side, the air blowing performance is improved, and the separation and turbulence of the air flow near the side plate 16 are suppressed. By doing so, it is possible to reduce turbulent noise and further prevent the heat exchange amount of the heat exchanger 6 from being reduced.

【００４９】（実施例３）図１２は本発明の実施例３に
おける空気調和機に搭載した遠心送風機の羽根車の構造
を、図１３は図１２の同実施例３における遠心送風機の
羽根車の斜視図を、また、図１４は図１２の同実施例３
における遠心送風機の羽根車のＨ−Ｈ断面を、さらにま
た、図１５は図１２の同実施例３における遠心送風機の
羽根車の部分正面図を示すものである。(Embodiment 3) FIG. 12 shows the structure of an impeller of a centrifugal blower mounted on an air conditioner in Embodiment 3 of the present invention, and FIG. 13 shows the structure of the impeller of the centrifugal blower in Embodiment 3 of FIG. FIG. 14 is a perspective view, and FIG.
FIG. 15 is a partial front view of the impeller of the centrifugal blower according to the third embodiment shown in FIG.

【００５０】図において、本発明の実施例１における空
気調和機からさらに、羽根板１８の後縁部において、側
板１９と羽根板１８との結合端部１８ｓの位置を主板２
０と羽根板１８との結合端部１８ｈの位置より回転方向
とは逆向きの位置に設定し、主板２０から側板１９まで
の羽根板１８の後縁部を連続的に変化させている。In the drawing, the position of the connecting end 18 s between the side plate 19 and the blade plate 18 at the rear edge of the blade plate 18 is further changed from the air conditioner according to the first embodiment of the present invention to the main plate 2.
A position opposite to the rotation direction is set to a position opposite to the rotation direction from the position of the coupling end 18 h between the zero and the blade 18, and the rear edge of the blade 18 from the main plate 20 to the side plate 19 is continuously changed.

【００５１】以上のように構成された空気調和機につい
て以下その動作を説明する。まず、電動機５の駆動力に
よって羽根車２１が所定の回転方向に回転すると、空気
が吸込みリング８を介して羽根車２１内に流入され、複
数の羽根板１８の間を通過する際に静圧と動圧を付加さ
れ、さらに、熱交換器６を通過する際に加熱または冷却
され、吹出口９より吹き出されて、室内温度と室内湿度
を調整する作用を為す。The operation of the air conditioner configured as described above will be described below. First, when the impeller 21 rotates in a predetermined rotation direction by the driving force of the electric motor 5, air flows into the impeller 21 through the suction ring 8, and when passing between the plurality of impellers 18, static pressure is applied. Further, it is heated or cooled when passing through the heat exchanger 6 and is blown out from the blow-out port 9 to adjust the room temperature and the room humidity.

【００５２】ここで、羽根板１８の後縁部において、側
板１９と羽根板１８との結合端部１８ｓの位置を主板２
０と羽根板１８との結合端部１８ｈの位置より回転方向
とは逆向きの位置に設定し、主板２０から側板１９まで
の羽根板１８の後縁部を連続的に変化させたので、羽根
板１８を通過する気流に対して働く力の作用は、回転軸
に垂直な平面内の成分のみでなく、主板２０側から側板
１９側へ向かう成分も生じるため、気流が側板１９側に
偏り側板１９側の流速を増速させ、図１６に示すように
羽根車２１出口における気流速度分布を均一化すること
になる。Here, at the rear edge of the slat 18, the position of the connection end 18 s between the side plate 19 and the slat 18 is determined by the main plate 2.
Since the rotation direction is set to a position opposite to the direction of rotation from the position of the coupling end 18h between the zero and the blade 18 and the rear edge of the blade 18 from the main plate 20 to the side plate 19 is continuously changed. The action of the force acting on the airflow passing through the plate 18 includes not only a component in a plane perpendicular to the rotation axis but also a component directed from the main plate 20 side to the side plate 19 side. By increasing the flow velocity on the 19 side, the air flow velocity distribution at the exit of the impeller 21 is made uniform as shown in FIG.

【００５３】そのため、送風性能を改善し、速板１９近
傍の気流の剃離と乱れを抑制することにより乱流騒音を
低減し、さらに、熱交換器６の熱交換量が低下するのを
防止することができる。For this reason, the air blowing performance is improved, the turbulence noise is reduced by suppressing the shaving and turbulence of the air flow near the speed plate 19, and the heat exchange amount of the heat exchanger 6 is prevented from being reduced. can do.

【００５４】また、遠心送風機の羽根車２１が設計動作
点より高静圧条件下で使用される場合、羽根車２１を通
過する空気の流量が減少して、羽根車２１へ流入する気
流の速度が小さくなるため、速板１９の吸込口を流れる
流入気流に対して働く力の作用は、軸方向成分が減少
し、羽根板１８の吸引力により発生する半径方向成分が
大きくなった結果、側板１９の吸込口において羽根車２
１内に流入しようとする気流は、既に羽根車２１の出口
方向に傾いた流れとなる。When the impeller 21 of the centrifugal blower is used under conditions of higher static pressure than the design operating point, the flow rate of air passing through the impeller 21 decreases, and the speed of the airflow flowing into the impeller 21 decreases. Is reduced, the effect of the force acting on the inflow airflow flowing through the suction port of the speed plate 19 is such that the axial component is reduced and the radial component generated by the suction force of the blade plate 18 is increased. Impeller 2 at the 19 inlet
The airflow that is going to flow into 1 has already been inclined toward the exit of the impeller 21.

【００５５】よって、側板１９側と主板２０側との気流
の曲率差が小さくなり、側板１９の近傍では羽根板１８
に流入する気流の速度が大きくなるため、羽根車２１の
出口における気流速度が側板１９側で逆に大きくなろう
とするが、上端部を羽根車２１の回転方向に傾斜させた
羽根板１８に導かれ羽根負圧面１８ａおよび羽根加圧面
１８ｂに付着した気流Ｒは、主板２０側へと流れるた
め、側板１９側での吹出気流速度が大きくなりすぎるの
を抑制する効果が得られる。Accordingly, the difference in the curvature of the airflow between the side plate 19 and the main plate 20 is reduced, and the blade plate 18 is provided near the side plate 19.
The airflow velocity at the outlet of the impeller 21 tends to increase on the side of the side plate 19 because the velocity of the airflow flowing into the impeller 21 increases, but the upper end is guided to the impeller 18 inclined in the rotation direction of the impeller 21. Since the airflow R attached to the blade negative pressure surface 18a and the blade pressing surface 18b flows toward the main plate 20, the effect of suppressing the blowout airflow velocity at the side plate 19 from becoming too large can be obtained.

【００５６】さらにまた、羽根板１８の後縁部におい
て、側板１９と羽根板１８との結合端部１８ｓの位置を
主板２０と羽根板１８との結合端部１８ｈの位置より回
転方向とは逆向きの位置に設定するため、羽根車２１の
回転軸に直交する各羽根断面において、各羽根入口断面
を主板２０近傍の羽根入口断面に内包させ、側板１９近
傍羽根断面の羽根出口角を主板２０近傍羽根断面の羽根
出口角より小さくする場合がある。Further, at the trailing edge of the wing plate 18, the position of the connecting end 18s between the side plate 19 and the wing plate 18 is opposite to the rotational direction from the position of the connecting end 18h between the main plate 20 and the wing plate 18. In order to set the orientation of the blade, in each blade section orthogonal to the rotation axis of the impeller 21, each blade inlet section is included in the blade inlet section near the main plate 20, and the blade outlet angle of the blade section near the side plate 19 is set as the main plate 20. In some cases, the blade exit angle may be smaller than the blade exit angle of the nearby blade section.

【００５７】この場合、遠心送風機の羽根車２１が設計
動作点より高静圧条件下での使用となった時、主板２０
近傍羽根断面の羽根出口角を大きく設定したことによ
り、主板２０側の羽根負圧面にて気流の剃離が発生し、
乱れが増加しようとするが、上端部を羽根車２１の回転
方向に傾斜させた羽根板１８に導かれ羽根負圧面１８ａ
に付着した気流Ｒは、主板２０側の羽根負圧面部まで流
れるため、気流が剃離しようとするのを抑制する効果が
得られる。In this case, when the impeller 21 of the centrifugal blower is used under high static pressure conditions from the design operating point, the main plate 20
By setting the blade exit angle of the vicinity blade cross section to be large, separation of air flow occurs on the blade negative pressure surface on the main plate 20 side,
Although the turbulence tends to increase, the upper end portion is guided to the blade plate 18 whose inclination is inclined in the rotation direction of the impeller 21, and the blade negative pressure surface 18 a
The airflow R attached to the main plate 20 flows to the blade negative pressure surface portion on the main plate 20 side, so that an effect of suppressing an attempt to separate the airflow can be obtained.

【００５８】従って、羽根車２１が設計動作点より高静
圧条件下で使用される場合でも、羽根板１８の上端部か
らの流入気流Ｒが羽根負圧面１８ａに付着し、羽根板１
８に沿って流れ、羽根板１８の上端部からの流入気流を
羽根負圧面１８ａに付着させ、さらに、羽根板１８を通
過する気流に対して働く力の作用は、主板２０側から側
板１９側へ向かう成分にも生じるため、気流が側板１９
側に偏り側板１９側の流速を増側させ、羽根車２１出口
における気流速度分布を均一化することになる。Therefore, even when the impeller 21 is used under the condition of higher static pressure than the design operating point, the inflow airflow R from the upper end of the blade plate 18 adheres to the blade negative pressure surface 18a, and the blade plate 1
8, the inflow airflow from the upper end of the blade plate 18 adheres to the blade negative pressure surface 18a, and the action of the force acting on the airflow passing through the blade plate 18 is from the main plate 20 side to the side plate 19 side. The airflow is also generated in the component going to
Thus, the flow velocity on the side plate 19 side is increased, and the airflow velocity distribution at the exit of the impeller 21 is made uniform.

【００５９】そのため、送風性能を改善し、側板１９近
傍の気流の剃離と乱れを抑制することにより乱流騒音を
低減し、さらに、熱交換器６の熱交換量が低下するのを
防止することができる。Therefore, the air blowing performance is improved, the turbulence noise is reduced by suppressing the shaving and turbulence of the air flow near the side plate 19, and the heat exchange amount of the heat exchanger 6 is prevented from being reduced. be able to.

【００６０】以上のように本実施例によれば、羽根板１
８の高縁部において、側板１９と羽根板１８との結合端
部１８ｓの位置を主板２０と羽根板１８との結合端部１
８ｈの位置より回転方向とは逆向きの位置に設定し、主
板２０から側板１９までの羽根板１８の後縁部を連続的
に変化させることにより、羽根車２１が設計動作点より
高静圧条件下で使用される場合でも、羽根板１８の上端
部からの流入気流Ｒが羽根負圧面１８ａに付着し、さら
に、羽根板１８を通過する気流に対して働く力の作用
は、主板２０側から側板１９側へ向かう成分にも生じる
ため、羽根車２１出口における気流速度分布を均一化す
ることになる。As described above, according to this embodiment, the blade 1
8, the position of the connecting end 18s between the side plate 19 and the wing plate 18 is changed to the connecting end 1 between the main plate 20 and the wing plate 18.
8h, a position opposite to the rotation direction is set, and the trailing edge of the blade plate 18 from the main plate 20 to the side plate 19 is continuously changed, so that the impeller 21 has a higher static pressure than the design operating point. Even when used under the conditions, the inflow airflow R from the upper end of the blade plate 18 adheres to the blade negative pressure surface 18a, and furthermore, the action of the force acting on the airflow passing through the blade plate 18 depends on the main plate 20 side. The airflow velocity distribution at the exit of the impeller 21 is also uniformized because the airflow component is also generated in the component traveling from the side to the side plate 19 side.

【００６１】そのため、送風性能を改善し、側板１９近
傍の気流の剃離と乱れを抑制することにより乱流騒音を
低減し、さらに、熱交換器６の熱交換量が低下するのを
防止することができる。For this reason, the air blowing performance is improved, the turbulence noise is reduced by suppressing the separation and turbulence of the air flow near the side plate 19, and the heat exchange amount of the heat exchanger 6 is prevented from being reduced. be able to.

【００６２】なお、実施例１、実施例２、実施例３で
は、遠心送風機の羽根車の羽根断面形状を略平板形状と
したが、図１７に示すように、翼型形状とすることによ
り、さらに、羽根板２２の上端部からの流入気流ｓを偏
向させ、羽根板２２の上端部を傾斜させた羽根負圧面２
２ａに気流を導き、さらに下流側の羽根板２２の略垂直
部分の羽根負圧面２２ｂに安定した気流を確実に案内す
るため、羽根板２２の羽根負圧面での気流の剃離を抑制
する効果を高め、送風性能の低下および乱流騒音の増加
を抑えることができる。In the first, second and third embodiments, the impeller of the centrifugal blower has a substantially flat cross-sectional shape. However, as shown in FIG. Furthermore, the inflow airflow s from the upper end portion of the blade plate 22 is deflected, and the upper end portion of the blade plate 22 is inclined so that the blade negative pressure surface 2 is inclined.
2a, the air flow is guided to the blade negative pressure surface 22b in the substantially vertical portion of the blade plate 22 on the downstream side, and the stable air flow is reliably guided to the blade negative pressure surface of the blade plate 22. And a decrease in the blowing performance and an increase in turbulent noise can be suppressed.

【００６３】なおまた、実施例１、実施例２、実施例３
では、羽根板の上端部を羽根車の回転方向に傾斜させる
ための具体的設定方法は特に限定していないが、図１
８、図１９、図２０に示すように、羽根車２３の軸心と
同心となる円筒状に切断した時のＩ−Ｉ断面を平面状に
展開した羽根断面形状において、羽根車２３の回転軸と
羽根板２４の上端部とのなす傾斜角度γを、図２１に示
すように羽根車２３の内周側から外周側にかけて大きく
なるように設定することにより、羽根車２３の内周側か
ら外周側にかけて流入気流角度が変化する羽根板２４の
上端部からの流入気流Ｔにあわせて、羽根板２４の上端
部を傾斜させることができる。Further, Embodiments 1, 2, and 3
Although a specific setting method for inclining the upper end of the impeller in the rotation direction of the impeller is not particularly limited, FIG.
As shown in FIGS. 8, 19 and 20, the rotation axis of the impeller 23 in the cross-sectional shape of the impeller 23 when the cross section taken along a line I-I developed concentrically with the axis of the impeller 23 is developed into a planar shape. And the upper end of the blade plate 24 are set so as to increase from the inner peripheral side to the outer peripheral side of the impeller 23 as shown in FIG. The upper end of the blade plate 24 can be inclined in accordance with the inflow airflow T from the upper end of the blade plate 24 in which the inflow airflow angle changes toward the side.

【００６４】この流入気流角度の変化は、羽根車２３を
通過する気流が、羽根車２３の軸方向から流入し、軸と
直交する方向へと流出することになるため、遠心力によ
り気流が流れ外周側である主板側に偏り、それに伴い羽
根板２４の上端部から流入する気流Ｔも主板２５側に偏
り、羽根車２３の内周側から外周側にかけて流入気流Ｔ
の軸方向速度が減少すめために発生するものであり、そ
の結果、羽根板２４上端部への流入気流角度γも羽根車
２３の内周側から外周側にかけて大きくなる。The change in the inflow airflow angle is caused by the fact that the airflow passing through the impeller 23 flows in the axial direction of the impeller 23 and outflows in a direction perpendicular to the axis. The airflow T flowing from the upper end portion of the blade plate 24 is also biased toward the main plate 25, and the inflow airflow T flows from the inner circumference side to the outer circumference side of the impeller 23.
As a result, the inflow airflow angle γ to the upper end of the blade plate 24 also increases from the inner peripheral side to the outer peripheral side of the impeller 23.

【００６５】よって、羽根板２４の上端部からの流入気
流Ｔを偏向させ、羽根板２４の上端部を傾斜させた羽根
負圧面に気流を導き、さらに下流側の羽根板２４の略垂
直部分の羽根負圧面２４ｂに安定した気流を確実に案内
するため、羽根板２４の羽根負圧面での気流の剃離を抑
制することができる。Therefore, the inflow airflow T from the upper end of the blade plate 24 is deflected, and the airflow is guided to the blade negative pressure surface in which the upper end of the blade plate 24 is inclined. In order to reliably guide the stable airflow to the blade negative pressure surface 24b, it is possible to suppress the separation of the airflow on the blade negative pressure surface of the blade plate 24.

【００６６】なおさらに、実施例１、実施例２、実施例
３では、羽根板の上端部を羽根車の回転方向に傾斜させ
るための具体的設定方法は特に限定していないが、図２
２、図２３、図２４に示すように、羽根車２６の軸心と
同心となる円筒状に切断した時のＪ−Ｊ断面を平面状に
展開した羽根断面形状において、羽根車２６の回転軸と
羽根板２７の上端部とのなす傾斜角度γを、図２５に示
すように羽根車２６の内周側から外周側にかけて大きく
なるように設定し、側板２８近傍では小さくなるよう設
定することにより、羽根車２６の内周側から外周側にか
けて流入気流角度が変化する羽根板２７上端部からの流
入気流Ｕにあわせて、羽根板２７の上端部を傾斜させる
ことができる。Further, in the first, second and third embodiments, the specific setting method for inclining the upper end portion of the blade plate in the rotation direction of the impeller is not particularly limited, but FIG.
2. As shown in FIGS. 23 and 24, the rotation axis of the impeller 26 is a blade cross-sectional shape in which a JJ cross section when cut into a cylindrical shape concentric with the axis of the impeller 26 is developed into a planar shape. And the upper end of the blade plate 27 are set to increase from the inner circumference to the outer circumference of the impeller 26 as shown in FIG. The upper end of the blade plate 27 can be inclined in accordance with the inflow airflow U from the upper end of the blade plate 27 where the inflow airflow angle changes from the inner peripheral side to the outer peripheral side of the impeller 26.

【００６７】この流入気流角度の変化は、羽根車２６を
通過する気流が、羽根車２６の軸方向から流入し、軸と
垂直となる方向へと流出することになるため、遠心力に
より気流が流れ外周側である主板２９側に偏る。それに
伴い羽根板２７の上端部から流入する気流Ｕも主板２９
側に偏るため、羽根車２６の内周側から外周側にかけて
軸方向速度が減少し、さらには、側板２８近傍では流入
気流Ｕは側板２８の壁面に付着して安定して流れるため
に軸方向速度は増加するために発生するものであり、そ
の結果、羽根板２７上端部への流入気流角度も羽根車２
６の内周側から外周側にかけて大きくなり、側板２８近
傍で小さくなる。This change in the inflow airflow angle is caused by the fact that the airflow passing through the impeller 26 flows in the axial direction of the impeller 26 and outflows in a direction perpendicular to the axis. The flow is biased toward the main plate 29 which is the outer peripheral side of the flow. Accordingly, the airflow U flowing from the upper end of the blade plate 27 is also
As a result, the axial velocity decreases from the inner peripheral side to the outer peripheral side of the impeller 26. Further, in the vicinity of the side plate 28, the inflow airflow U adheres to the wall surface of the side plate 28 and flows in a stable manner in the axial direction. The speed is generated because the speed increases, and as a result, the inflow airflow angle to the upper end of the blade plate 27 also increases.
6 increases from the inner circumference to the outer circumference, and decreases near the side plate 28.

【００６８】よって、羽根板２７の上端部からの流入気
流Ｕを偏向させ、羽根板２７の上端部を傾斜させた羽根
負圧面２７ａに気流を導き、さらに下流側の羽根板２７
の略垂直部分の羽根負圧面２７ｂに安定した気流を確実
に案内するため、羽根板２７の羽根負圧面での気流の剃
離を抑制する。Therefore, the inflow air flow U from the upper end of the blade plate 27 is deflected, and the air flow is guided to the blade negative pressure surface 27a in which the upper end of the blade plate 27 is inclined.
In order to reliably guide a stable airflow to the blade negative pressure surface 27b of the substantially vertical portion, shaving of the airflow on the blade negative pressure surface of the blade plate 27 is suppressed.

【００６９】また、実施例２と、実施例３との組み合わ
せにより、より高い性能改善効果が得られることは容易
に考えられる。It is easily conceivable that a higher performance improving effect can be obtained by the combination of the second embodiment and the third embodiment.

【００７０】[0070]

【発明の効果】以上のように請求項１に記載の発明は、
複数の羽根板と、前記羽根板を固定した主板と、前記羽
根板の反主板側端部に固定した吸込口を有する側板とで
形成してなる遠心送風機の羽根車と、前記側板の吸込口
に挿入した吸込リングと、前記羽根車の吹出側に配設し
た略環状の熱交換器と、前記羽根車と前記吸込リングと
前記熱交換器とを内部におさめたケーシングで構成され
た空気調和機において、前記羽根板の上端部を前記羽根
車の回転方向に傾斜させているので、羽根板の上端部か
らの流入気流を偏向させ、羽根板の上端部を傾斜させた
部分の羽根負圧面に気流を導き、さらに、下流側の羽根
板の略垂直部分の羽根負圧面に安定した気流を案内する
ため、羽根負圧面での気流の剃離を抑制することがで
き、羽根車の設計動作点より高静圧な動作点で作動する
場合でも送風能力の低下を抑制すると共に、流れの剃離
に伴う乱流騒音の増加を抑えることができる。As described above, the invention according to claim 1 is
A plurality of blades, a main plate to which the blades are fixed, and a side plate having a suction port fixed to an end of the blades at a side opposite to the main plate, and an impeller of a centrifugal blower formed by a suction port of the side plates. An air conditioner comprising: a suction ring inserted into the impeller; a substantially annular heat exchanger disposed on the outlet side of the impeller; and a casing containing the impeller, the suction ring, and the heat exchanger therein. In the machine, since the upper end of the blade plate is inclined in the rotation direction of the impeller, the inflow airflow from the upper end of the blade plate is deflected, and the blade negative pressure surface of the portion where the upper end of the blade plate is inclined is provided. In order to guide the air flow to the blade negative pressure surface in a substantially vertical part of the downstream blade plate and to guide the stable air flow to the blade negative pressure surface, it is possible to suppress the separation of the air flow at the blade negative pressure surface, and the design operation of the impeller Even when operating at an operating point with a higher static pressure than the Suppresses the lower, it is possible to suppress an increase in turbulence noise caused by the flow of SuHanare.

【００７１】また、請求項２に記載の発明は、請求項１
に記載の発明からさらに、羽根車の回転軸に直交する羽
根断面において、側板近傍羽根断面の羽根出口角を主板
近傍羽根断面の羽根出口角より大きく設定し、前記主板
から前記側板までの羽根断面形状を連続的に変化させて
いるので、側板側の羽根板の仕事量を主板側の羽根仕事
量より増加させて側板側の流速を増速させ羽根車出口に
おける気流速度分布を均一化することになるため、送風
性能を改善し、側板近傍の気流の剃離と乱れを抑制する
ことにより乱流騒音を低減し、さらに、熱交換器の熱交
換量が低下するのを防止することができる。The invention according to claim 2 is the same as the invention according to claim 1.
Further, in the blade section orthogonal to the rotation axis of the impeller, the blade exit angle of the blade section near the side plate is set to be larger than the blade exit angle of the blade section near the main plate, and the blade section from the main plate to the side plate. Since the shape is continuously changed, the work volume of the blades on the side plate side should be increased from the work volume of the blades on the main plate side to increase the flow velocity on the side plate side and make the airflow velocity distribution at the exit of the impeller uniform. Therefore, it is possible to improve the air blowing performance, reduce the turbulent noise by suppressing the turbulence and turbulence of the air flow near the side plate, and further prevent the heat exchange amount of the heat exchanger from being reduced. .

【００７２】また、遠心送風機の羽根車が設計動作点よ
り高静圧条件下で使用される場合、羽根車の出口におけ
る気流速度が側板側で逆に大きくなろうとするが、羽根
板の上端部の羽根負圧面および羽根加圧面に付着した気
流は、主板側へと流れるため、側板側での吹出気流速度
が大きくなりすぎのを抑制する効果が得られる。When the impeller of the centrifugal blower is used under conditions of higher static pressure than the design operating point, the airflow velocity at the exit of the impeller tends to increase on the side plate side. The airflow adhering to the blade negative pressure surface and the blade pressing surface flows to the main plate side, so that the effect of suppressing the blowout airflow velocity at the side plate side from becoming too large can be obtained.

【００７３】さらにまた、遠心送風機の羽根車が設計動
作点より高静圧条件下で使用される場合、側板側の羽根
負圧面にて気流の剥離が発生し、乱れが増加しようとす
るが、羽根板上端部の羽根負圧面に付着した気流は、側
板側の羽根負圧面部を流れるため、気流が剃離しようと
するのを抑制する効果が得られる。Further, when the impeller of the centrifugal blower is used under the condition of high static pressure from the design operating point, the air flow is separated on the blade negative pressure surface on the side plate side, and the turbulence tends to increase. Since the airflow adhering to the blade negative pressure surface at the upper end portion of the blade plate flows through the blade negative pressure surface portion on the side plate side, an effect of suppressing the airflow from being separated is obtained.

【００７４】また、請求項３に記載の発明は、請求項１
に記載の発明からさらに、羽根板の後縁部において、側
板と前記羽根板との結合端部の位置を主板と前記羽根板
との結合端部の位置より回転方向とは逆向きの位置に設
定し、前記主板から前記側板までの前記羽根板の後縁部
を連続的に変化させているので、気流が側板側に偏り、
側板側の流速を増側させ羽根車出口における気流速度分
布を均一化することになるため、送風性能を改善し、側
板近傍の気流の剃離と乱れを抑制することにより乱流騒
音を低減し、さらに、熱交換器の熱交換量が低下するの
を防止することができる。The third aspect of the present invention is the first aspect of the present invention.
Further, from the invention described in the above, at the trailing edge of the blade plate, the position of the coupling end between the side plate and the blade plate is in a position opposite to the rotational direction from the position of the coupling end between the main plate and the blade plate. Setting, since the trailing edge of the blade plate from the main plate to the side plate is continuously changed, the airflow is biased to the side plate side,
Since the flow velocity on the side plate side is increased and the air flow velocity distribution at the impeller outlet is made uniform, the ventilation performance is improved, and the turbulence noise is reduced by suppressing the separation and turbulence of the air flow near the side plate. Further, it is possible to prevent the heat exchange amount of the heat exchanger from being reduced.

【００７５】また、遠心送風機の羽根車が設計動作点よ
り高静圧条件下で使用される場合、羽根車の出口におけ
る気流速度が側板側で逆に大きくなろうとするが、羽根
板の上端部の羽根負圧面および羽根加圧面に付着した気
流は、主板側へと流れるため、側板側での吹出気流速度
が大きくなりすぎるのを抑制する効果が得られる。When the impeller of the centrifugal blower is used under conditions of higher static pressure than the design operating point, the airflow velocity at the outlet of the impeller tends to increase on the side plate side. The airflow adhering to the blade negative pressure surface and the blade pressing surface flows to the main plate side, so that an effect of suppressing the blowout airflow velocity at the side plate side from becoming too large can be obtained.

【００７６】さらにまた、側板と羽根板との結合端部の
位置を主板と羽根板との結合端部の位置より回転方向と
は逆向きの位置に設定するため、側板近傍羽根断面の羽
根出口角を主板近傍羽根断面の羽根出口角より小さくす
る場合、遠心送風機の羽根車が設計動作点より高静圧条
件下での使用となった時、主板側の羽根負圧面にて気流
の剃離が発生し、乱れが増加しようとするが、羽根板上
端部の羽根負圧面に付着した気流は、主板側の羽根負圧
面部まで流れるため、気流が剃離しようとするのを抑制
する効果が得られる。Furthermore, since the position of the joint end between the side plate and the blade plate is set to a position opposite to the rotational direction from the position of the joint end between the main plate and the blade plate, the blade outlet in the cross section of the blade near the side plate is set. When the angle is smaller than the blade exit angle of the blade section near the main plate, when the impeller of the centrifugal blower is used under high static pressure condition from the design operating point, the air flow is separated at the blade negative pressure surface on the main plate side Is generated, and the turbulence tends to increase.However, since the airflow adhering to the blade negative pressure surface at the upper end of the blade flows to the blade negative pressure surface on the main plate side, the effect of suppressing the airflow from being separated is effective. can get.

【図面の簡単な説明】[Brief description of the drawings]

【図１】本発明の実施例１における空気調和機の断面図FIG. 1 is a sectional view of an air conditioner according to a first embodiment of the present invention.

【図２】本発明の実施例１における空気調和機に搭載し
た遠心送風機の羽根車の斜視図FIG. 2 is a perspective view of an impeller of a centrifugal blower mounted on the air conditioner according to the first embodiment of the present invention.

【図３】本発明の実施例１における空気調和機搭載した
遠心送風機の羽根車要部詳細図FIG. 3 is a detailed view of a main part of an impeller of the centrifugal blower mounted with the air conditioner according to the first embodiment of the present invention.

【図４】本発明の実施例１における空気調和機に搭載し
た遠心送風機の羽根車のＤ−Ｄ線要部断面図FIG. 4 is a cross-sectional view of a main part of a centrifugal blower impeller mounted on the air conditioner according to the first embodiment of the present invention, taken along line D-D.

【図５】本発明の実施例１における空気調和機に搭載し
た遠心送風機の羽根車のＤ１／Ｄ２を変えたときの最高
効率点での騒音値を示す実験結果による特性図FIG. 5 is a characteristic diagram based on experimental results showing noise values at the highest efficiency point when D1 / D2 of the impeller of the centrifugal blower mounted on the air conditioner according to the first embodiment of the present invention is changed.

【図６】本発明の実施例２における空気調和機に搭載し
た遠心送風機の羽根車要部詳細図FIG. 6 is a detailed view of a main part of an impeller of a centrifugal blower mounted on an air conditioner according to a second embodiment of the present invention.

【図７】本発明の実施例２における空気調和機に搭載し
た遠心送風機の羽根車の斜視図FIG. 7 is a perspective view of an impeller of a centrifugal blower mounted on an air conditioner according to Embodiment 2 of the present invention.

【図８】本発明の実施例２における空気調和機に搭載し
た遠心送風機の羽根車のＥ−Ｅ線要部断面図FIG. 8 is a cross-sectional view of a main part of the impeller of the centrifugal blower mounted on the air conditioner according to the second embodiment of the present invention along line EE.

【図９】本発明の実施例２における空気調和機に搭載し
た遠心送風機の羽根車のＦ−Ｆ線要部断面図FIG. 9 is a cross-sectional view of a main part of an impeller of a centrifugal blower mounted on an air conditioner according to a second embodiment of the present invention, taken along line FF.

【図１０】本発明の実施例２における空気調和機に搭載
した遠心送風機の羽根車のＧ−Ｇ線要部断面図FIG. 10 is a cross-sectional view of a main part of the impeller of the centrifugal blower mounted on the air conditioner according to the second embodiment of the present invention along line GG.

【図１１】本発明の実施例２における空気調和機に搭載
した遠心送風機の羽根車出口の気流速度分布を示す模式
図FIG. 11 is a schematic diagram showing an airflow velocity distribution at an impeller outlet of a centrifugal blower mounted on an air conditioner according to Embodiment 2 of the present invention.

【図１２】本発明の実施例３における空気調和機に搭載
した遠心送風機の羽根車要部詳細図FIG. 12 is a detailed view of a main part of an impeller of a centrifugal blower mounted on an air conditioner according to a third embodiment of the present invention.

【図１３】本発明の実施例３における空気調和機に搭載
した遠心送風機の羽根車の斜視図FIG. 13 is a perspective view of an impeller of a centrifugal blower mounted on an air conditioner according to Embodiment 3 of the present invention.

【図１４】本発明の実施例３における空気調和機に搭載
した遠心送風機の羽根車のＨ−Ｈ線要部断面図FIG. 14 is a cross-sectional view of a main part of the impeller of the centrifugal blower mounted on the air conditioner according to the third embodiment of the present invention, taken along line HH.

【図１５】本発明の実施例３における空気調和機に搭載
した遠心送風機の羽根車の部分正面図FIG. 15 is a partial front view of an impeller of a centrifugal blower mounted on an air conditioner according to Embodiment 3 of the present invention.

【図１６】本発明の実施例３における空気調和機に搭載
した遠心送風機の羽根車出口の気流速度分布を示す模式
図FIG. 16 is a schematic diagram showing an airflow velocity distribution at an impeller outlet of a centrifugal blower mounted on an air conditioner according to Embodiment 3 of the present invention.

【図１７】本発明の実施例３における空気調和機に搭載
した遠心送風機の羽根車のＨ−Ｈ線要部断面図FIG. 17 is a cross-sectional view of the main part of the impeller of the centrifugal blower mounted on the air conditioner according to the third embodiment of the present invention, taken along line HH.

【図１８】本発明の実施例３における空気調和機に搭載
した遠心送風機の羽根車要部詳細図FIG. 18 is a detailed view of a main part of an impeller of a centrifugal blower mounted on an air conditioner according to a third embodiment of the present invention.

【図１９】本発明の実施例３における空気調和機に搭載
した遠心送風機の羽根板の断面図FIG. 19 is a cross-sectional view of a blade of a centrifugal blower mounted on an air conditioner according to Embodiment 3 of the present invention.

【図２０】本発明の実施例３における空気調和機に搭載
した遠心送風機の羽根車のＩ−Ｉ線要部断面図FIG. 20 is a cross-sectional view of a main part of the impeller of the centrifugal blower mounted on the air conditioner according to the third embodiment of the present invention, taken along line II.

【図２１】本発明の実施例３における遠心送風機の羽根
板の上端部の傾斜角度分布特性図FIG. 21 is an inclination angle distribution characteristic diagram of the upper end portion of the blade of the centrifugal blower according to the third embodiment of the present invention.

【図２２】本発明の実施例３における空気調和機に搭載
した遠心送風機の羽根車要部詳細図FIG. 22 is a detailed view of a main part of an impeller of a centrifugal blower mounted on an air conditioner according to Embodiment 3 of the present invention.

【図２３】本発明の実施例３における空気調和機に搭載
した遠心送風機の羽根板の断面図FIG. 23 is a sectional view of a blade of a centrifugal blower mounted on an air conditioner according to Embodiment 3 of the present invention.

【図２４】本発明の実施例３における空気調和機に搭載
した遠心送風機の羽根車のＪ−Ｊ線要部断面図FIG. 24 is a cross-sectional view of a main part of the impeller of the centrifugal blower mounted on the air conditioner according to the third embodiment of the present invention, taken along line JJ.

【図２５】本発明の実施例３における遠心送風機の羽根
板の上端部の傾斜角度分布特性図FIG. 25 is an inclination angle distribution characteristic diagram of the upper end of the blade of the centrifugal blower according to the third embodiment of the present invention.

【図２６】従来の空気調和機の断面図FIG. 26 is a sectional view of a conventional air conditioner.

【図２７】従来の空気調和機に搭載した遠心送風機の羽
根車要部詳細図FIG. 27 is a detailed view of a main part of an impeller of a centrifugal blower mounted on a conventional air conditioner.

【図２８】従来の空気調和機に搭載した遠心送風機の羽
根車のＡ−Ａ線要部断面図FIG. 28 is a cross-sectional view of a main part of an impeller of a centrifugal blower mounted on a conventional air conditioner, taken along line AA.

【図２９】従来の空気調和機に搭載した遠心送風機の羽
根車のＢ−Ｂ線要部断面図FIG. 29 is a cross-sectional view of a main part of the impeller of the centrifugal blower mounted on the conventional air conditioner, taken along line BB.

【図３０】従来の空気調和機に搭載した遠心送風機の羽
根車の部分正面図FIG. 30 is a partial front view of an impeller of a centrifugal blower mounted on a conventional air conditioner.

【図３１】従来の空気調和機に搭載した遠心送風機の羽
根車出口の気流速度分布を示す模式図FIG. 31 is a schematic view showing an airflow velocity distribution at an impeller outlet of a centrifugal blower mounted on a conventional air conditioner.

【符号の説明】[Explanation of symbols]

１０，１４，２１，２３，２６ 羽根車 １１，１５，１８，２２，２４，２７ 羽根板 １１ａ，１５ａ，１８ａ，２２ａ，２４ａ，２７ａ 羽
根板の上端部 １２，１７，２０，２５，２９ 主板 １３，１６，１９，２８ 側板 １８ｈ 主板側結合端部 １８ｓ 側板側結合部 βｈ 主板側羽根出口角 βｓ 側板側羽根出口角10, 14, 21, 23, 26 Impeller 11, 15, 18, 22, 24, 27 Impeller 11a, 15a, 18a, 22a, 24a, 27a Upper end of impeller 12, 17, 20, 25, 29 Main plate 13, 16, 19, 28 Side plate 18h Main plate side connection end 18s Side plate side connection βh Main plate side blade exit angle βs Side plate side blade exit angle

Claims (3)

【特許請求の範囲】[Claims] 【請求項１】 複数の羽根板と、前記羽根板を固定した
主板と、前記羽根板の反主板側端面に固定した吸込口を
有する側板とで形成してなる遠心送風機の羽根車と、前
記側板の吸込口に挿入した吸込リングと、前記羽根車の
吹出側に配設した略環状の熱交換器と、前記羽根車と前
記吸込リングと前記熱交換器とを内部におさめたケーシ
ングで構成された空気調和機において、前記羽根板の上
端部を前記羽根車の回転方向に構成された空気調和機。1. A centrifugal fan impeller comprising: a plurality of blades; a main plate to which the blades are fixed; and a side plate having a suction port fixed to an end surface of the blades on the side opposite to the main plate; A suction ring inserted into the suction port of the side plate, a substantially annular heat exchanger disposed on the outlet side of the impeller, and a casing containing the impeller, the suction ring, and the heat exchanger therein. An air conditioner in which the upper end of the blade plate is arranged in the rotation direction of the impeller. 【請求項２】 羽根車の回転軸に直交する羽根断面にお
いて、側板近傍羽根断面の羽根出口角を主板近傍羽根断
面の羽根出口角より大きく設定し、前記主板から前記側
板までの羽根断面形状を連続的に変化させた請求項１記
載の空気調和機。2. A blade cross section orthogonal to a rotation axis of an impeller, a blade outlet angle of a blade cross section near a side plate is set to be larger than a blade outlet angle of a blade cross section near a main plate, and a blade cross section from the main plate to the side plate is formed. The air conditioner according to claim 1, wherein the air conditioner is continuously changed. 【請求項３】 羽根板の後縁部において、側板と前記羽
根板との結合端部の位置を主板と前記羽根板との結合端
部の位置より回転方向とは逆向きの位置に設定し、前記
主板から前記側板までの前記羽根板の後縁部を連続的に
変化させた請求項１記載の空気調和機。3. A rear edge portion of the blade plate, wherein a position of a joint end between the side plate and the blade plate is set to a position opposite to a rotational direction from a position of a joint end between the main plate and the blade plate. The air conditioner according to claim 1, wherein a trailing edge of the blade from the main plate to the side plate is continuously changed.
JP9000053A 1997-01-06 1997-01-06 Air conditioner Pending JPH10196591A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP9000053A JPH10196591A (en) 1997-01-06 1997-01-06 Air conditioner

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP9000053A JPH10196591A (en) 1997-01-06 1997-01-06 Air conditioner

Publications (1)

Publication Number Publication Date
JPH10196591A true JPH10196591A (en) 1998-07-31

Family

ID=11463509

Family Applications (1)

Application Number Title Priority Date Filing Date
JP9000053A Pending JPH10196591A (en) 1997-01-06 1997-01-06 Air conditioner

Country Status (1)

Country Link
JP (1) JPH10196591A (en)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001087162A (en) * 1999-09-27 2001-04-03 Toto Ltd Human body dryer and method for designing the dryer
KR20010105606A (en) * 2000-05-16 2001-11-29 구자홍 Structure for backward curved centrifugal fan
US6370907B1 (en) * 1999-01-18 2002-04-16 Mitsubishi Denki Kabushiki Kaisha Air conditioner
JP2005320881A (en) * 2004-05-07 2005-11-17 Matsushita Electric Ind Co Ltd Turbo fan and air conditioner using the same
WO2009069606A1 (en) 2007-11-26 2009-06-04 Daikin Industries, Ltd. Centrifugal fan
JP2015102002A (en) * 2013-11-25 2015-06-04 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． Turbo-fan, and air conditioner using the same
CN107667225A (en) * 2015-05-22 2018-02-06 三星电子株式会社 Turbofan and the air regulator including turbofan
CN109340179A (en) * 2018-11-27 2019-02-15 苏州工业园区星德胜电机有限公司 A kind of high-intensitive centrifugal impeller and motor suitable for dust catcher

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6370907B1 (en) * 1999-01-18 2002-04-16 Mitsubishi Denki Kabushiki Kaisha Air conditioner
JP2001087162A (en) * 1999-09-27 2001-04-03 Toto Ltd Human body dryer and method for designing the dryer
KR20010105606A (en) * 2000-05-16 2001-11-29 구자홍 Structure for backward curved centrifugal fan
JP2005320881A (en) * 2004-05-07 2005-11-17 Matsushita Electric Ind Co Ltd Turbo fan and air conditioner using the same
JP4590923B2 (en) * 2004-05-07 2010-12-01 パナソニック株式会社 Turbofan and air conditioner using the same
WO2009069606A1 (en) 2007-11-26 2009-06-04 Daikin Industries, Ltd. Centrifugal fan
US8784060B2 (en) 2007-11-26 2014-07-22 Daikin Industries, Ltd. Centrifugal fan
JP2015102002A (en) * 2013-11-25 2015-06-04 三星電子株式会社Ｓａｍｓｕｎｇ Ｅｌｅｃｔｒｏｎｉｃｓ Ｃｏ．，Ｌｔｄ． Turbo-fan, and air conditioner using the same
CN107667225A (en) * 2015-05-22 2018-02-06 三星电子株式会社 Turbofan and the air regulator including turbofan
US10641280B2 (en) 2015-05-22 2020-05-05 Samsung Electronics Co., Ltd. Turbo fan and air conditioner including same
CN109340179A (en) * 2018-11-27 2019-02-15 苏州工业园区星德胜电机有限公司 A kind of high-intensitive centrifugal impeller and motor suitable for dust catcher
CN109340179B (en) * 2018-11-27 2024-05-10 星德胜科技(苏州)股份有限公司 High-strength centrifugal impeller and motor suitable for dust collector

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