JPH10196591A - Air conditioner - Google Patents
Air conditionerInfo
- 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
Links
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
- Air-Conditioning Room Units, And Self-Contained Units In General (AREA)
Abstract
Description
【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.
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)
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.
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.
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.
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) |
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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 |
-
1997
- 1997-01-06 JP JP9000053A patent/JPH10196591A/en active Pending
Cited By (12)
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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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