JP6250145B2 - Centrifugal blower and vacuum cleaner - Google Patents

Centrifugal blower and vacuum cleaner Download PDF

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JP6250145B2
JP6250145B2 JP2016517777A JP2016517777A JP6250145B2 JP 6250145 B2 JP6250145 B2 JP 6250145B2 JP 2016517777 A JP2016517777 A JP 2016517777A JP 2016517777 A JP2016517777 A JP 2016517777A JP 6250145 B2 JP6250145 B2 JP 6250145B2
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side plate
impeller
turning
diameter
trailing edge
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JPWO2015170401A1 (en
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加藤　康明
康明 加藤
光将 浜崎
光将 浜崎
関根　加津典
加津典 関根
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Mitsubishi Electric Home Appliance Co Ltd
Mitsubishi Electric Corp
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Mitsubishi Electric Home Appliance Co Ltd
Mitsubishi Electric Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Electric Suction Cleaners (AREA)

Description

この発明は、遠心型の羽根車を有する遠心送風機、及びそれを用いた電気掃除機に関するものである。   The present invention relates to a centrifugal blower having a centrifugal impeller and a vacuum cleaner using the centrifugal blower.

径方向寸法が限られた中で、空気に対して仕事をする羽根車の径を大きくとると、羽根車から流出した直後の気流を軸方向に曲げなくてはならない。この急激な曲がりによって生じる損失を低減することを目的として、従来の遠心送風機では、羽根車の主板の外周部を、吹出口のある軸方向へ向けて湾曲させている（例えば、特許文献１参照）。   If the diameter of the impeller that works on the air is increased while the radial dimensions are limited, the airflow immediately after flowing out of the impeller must be bent in the axial direction. In order to reduce the loss caused by this sudden bending, in the conventional centrifugal blower, the outer peripheral portion of the main plate of the impeller is curved toward the axial direction where the blower outlet is located (for example, see Patent Document 1). ).

特開平４−１６４１９４号公報JP-A-4-164194

上記のような従来の遠心送風機では、主板の外周部を羽根車の径方向外側へ延長しているため、羽根車の径に対し、空気に仕事を与える翼の径方向への寸法が小さくなり、羽根車の寸法に対して得られる仕事率が小さくなる。また、主板が空気に与える仕事は小さいため、空気の流れ方向を吹出口の方向に向ける効果も低い。   In the conventional centrifugal blower as described above, since the outer peripheral portion of the main plate extends outward in the radial direction of the impeller, the radial dimension of the blade that gives work to the air is smaller than the diameter of the impeller. The work rate obtained with respect to the dimensions of the impeller is reduced. Moreover, since the work which a main board gives to air is small, the effect of orienting the flow direction of air to the direction of a blower outlet is also low.

この発明は、上記のような課題を解決するためになされたものであり、羽根車から流出した直後の気流の方向を変えることによる損失を低減しつつ、送風効率を向上させることができる遠心送風機及びそれを用いた電気掃除機を得ることを目的とする。   This invention is made in order to solve the above problems, and is a centrifugal blower capable of improving the blowing efficiency while reducing the loss caused by changing the direction of the airflow immediately after flowing out from the impeller. And it aims at obtaining the vacuum cleaner using the same.

この発明に係る遠心送風機は、モータ、第１の側板と、第１の側板に対向する第２の側板と、第１の側板と第２の側板との間に保持されている複数の翼とを有しており、モータにより駆動される遠心型の羽根車、及び羽根車の外周を覆い、羽根車から流出された直後の気流の方向を羽根車の軸方向の一側である出口方向に変えるための転向風路を形成する形成部材を備え、第１の側板は、第２の側板よりも出口側に位置しており、翼は、羽根車の径方向の外側端部に位置する後縁を有しており、後縁は、羽根車の径方向の最も外側に位置する後縁先端を有しており、かつ、第２の側板に隣接する部分及び第１の側板に隣接する部分から後縁先端へ向けて羽根車の径方向外側へ突出しており、後縁先端の軸方向位置は、第１の側板の外周の軸方向位置と第２の側板の外周の軸方向位置との中央よりも出口側であり、転向風路は、羽根車の径方向外側に位置する転向部と、転向部の下流に位置し出口方向に沿って気流を導く排出ダクト部とを有しており、後縁先端は、第１の側板の外周よりも羽根車の径方向外側に位置しており、羽根車の回転時の後縁先端の軌跡の径は、転向部と排出ダクト部との接続面における排出ダクト部の内径よりも大きく外径よりも小さい。 The centrifugal blower according to the present invention includes a motor, a first side plate, a second side plate facing the first side plate, and a plurality of blades held between the first side plate and the second side plate. The centrifugal impeller driven by the motor and the outer periphery of the impeller are covered, and the direction of the airflow immediately after flowing out of the impeller is set to the exit direction which is one side in the axial direction of the impeller. A forming member that forms a turning air passage for changing, the first side plate is located on the outlet side of the second side plate, and the blade is located at the radially outer end of the impeller The rear edge has a rear edge tip located on the outermost side in the radial direction of the impeller, and a part adjacent to the second side plate and a part adjacent to the first side plate Projecting radially outward from the impeller toward the tip of the trailing edge, and the axial position of the tip of the trailing edge is the axial direction of the outer periphery of the first side plate Position and Ri outlet der than the center of the axial position of the outer periphery of the second side plate, turning air passage includes a turning section located radially outward of the impeller, the outlet direction is located downstream of the turning section A discharge duct portion that guides the airflow along the rear edge, and the trailing edge tip is located radially outside the impeller from the outer periphery of the first side plate, and the trailing edge tip when the impeller rotates The diameter of the trajectory is larger than the inner diameter of the discharge duct portion at the connection surface between the turning portion and the discharge duct portion and smaller than the outer diameter .

この発明の遠心送風機は、翼の後縁の形状が、第２の側板に隣接する部分から後縁先端へ向けて羽根車の径方向外側へ突出する形状となっており、かつ、後縁先端の軸方向位置が、第１の側板の外周の軸方向位置と第２の側板の外周の軸方向位置との中央よりも出口方向の下流側であるため、羽根車から流出した直後の気流の方向を変えることによる損失を低減しつつ、送風効率を向上させることができる。   In the centrifugal blower of the present invention, the shape of the trailing edge of the blade is a shape that protrudes radially outward of the impeller from the portion adjacent to the second side plate toward the leading edge, and the trailing edge tip Is located downstream of the center between the axial position of the outer periphery of the first side plate and the axial position of the outer periphery of the second side plate, so that the airflow immediately after flowing out of the impeller The air blowing efficiency can be improved while reducing the loss caused by changing the direction.

この発明の実施の形態１による遠心送風機の軸線に沿う断面図である。It is sectional drawing which follows the axis line of the centrifugal blower by Embodiment 1 of this invention. 図１の羽根車を示す斜視図である。It is a perspective view which shows the impeller of FIG. 実施の形態１の羽根車の外周形状の特徴を説明するための図１の部分拡大図である。FIG. 2 is a partially enlarged view of FIG. 1 for explaining the feature of the outer peripheral shape of the impeller of the first embodiment. 実施の形態１の羽根車と転向風路との関係、及び転向風路の形状の特徴を説明するための図１の部分拡大図である。It is the elements on larger scale of FIG. 1 for demonstrating the relationship between the impeller of Embodiment 1, and the turning wind path, and the characteristic of the shape of a turning wind path. 図１の遠心送風機を内蔵した電気掃除機を示す構成図である。It is a block diagram which shows the vacuum cleaner which incorporated the centrifugal blower of FIG.

以下、この発明を実施するための形態について、図面を参照して説明する。
実施の形態１．
図１はこの発明の実施の形態１による遠心送風機の軸線に沿う断面図（回転軸を通る平面（子午面）における断面図）である。図１に示す矢印は、この断面における空気の流れの方向を示している。Hereinafter, embodiments for carrying out the present invention will be described with reference to the drawings.
Embodiment 1 FIG.
1 is a cross-sectional view (cross-sectional view on a plane (meridian plane) passing through a rotation axis) of the centrifugal blower according to Embodiment 1 of the present invention. The arrows shown in FIG. 1 indicate the direction of air flow in this cross section.

モータ１は、モータ本体２と、モータ本体２から突出した出力軸３とを有している。羽根車４は、出力軸３に固定されており、モータ１により駆動されて回転軸５を中心として回転する。回転軸５は、出力軸３の軸線と一致している。   The motor 1 has a motor body 2 and an output shaft 3 protruding from the motor body 2. The impeller 4 is fixed to the output shaft 3, and is driven by the motor 1 to rotate around the rotation shaft 5. The rotating shaft 5 coincides with the axis of the output shaft 3.

ここでは、回転軸５に平行な方向を軸方向と呼び、回転軸５から離れる方向を径方向と呼ぶ。このため、図１では、上下方向が軸方向となり、左右方向が径方向となる。   Here, a direction parallel to the rotation shaft 5 is referred to as an axial direction, and a direction away from the rotation shaft 5 is referred to as a radial direction. For this reason, in FIG. 1, the vertical direction is the axial direction, and the horizontal direction is the radial direction.

羽根車４は、遠心型（遠心形態）であり、第１の側板６と、第１の側板６に対向する第２の側板７と、第１の側板６と第２の側板７との間に挟まれて保持されている複数の翼８とを有している。   The impeller 4 is a centrifugal type (centrifugal form), and is between a first side plate 6, a second side plate 7 that faces the first side plate 6, and between the first side plate 6 and the second side plate 7. And a plurality of wings 8 held between the two.

この例では、第１の側板６が出力軸３に連結されている。また、第２の側板７の中央に外気を羽根車４に取り込むための吸込口７ａが設けられている。これに対して、第２の側板７を出力軸３に連結し、第１の側板６に吸込口を設けてもよい。   In this example, the first side plate 6 is connected to the output shaft 3. A suction port 7 a for taking outside air into the impeller 4 is provided at the center of the second side plate 7. On the other hand, the second side plate 7 may be connected to the output shaft 3 and the first side plate 6 may be provided with a suction port.

モータ本体２の羽根車４側の端部には、内側フレーム９が固定されている。内側フレーム９の外周部には、内側フレーム円筒部９ａが形成されている。   An inner frame 9 is fixed to the end of the motor body 2 on the impeller 4 side. An inner frame cylindrical portion 9 a is formed on the outer peripheral portion of the inner frame 9.

羽根車４及び内側フレーム９の径方向外側には、形成部材（転向風路形成部材）１０が配置されている。形成部材１０は、羽根車４及び内側フレーム９の外周を覆っている。また、形成部材１０は、羽根車４及び内側フレーム９の径方向外側に、羽根車４から流出された直後の気流の方向を羽根車４の軸方向の一側である出口方向に変えるための転向風路１１を形成する。   A forming member (turning air passage forming member) 10 is disposed on the radially outer side of the impeller 4 and the inner frame 9. The forming member 10 covers the outer periphery of the impeller 4 and the inner frame 9. Further, the forming member 10 changes the direction of the airflow immediately after flowing out from the impeller 4 to the outlet direction which is one side in the axial direction of the impeller 4 on the radially outer side of the impeller 4 and the inner frame 9. A turning air passage 11 is formed.

出口方向は、転向風路１１により向けられる気流の方向であり、図１では下方向である。第１の側板６は、第２の側板７よりも出口方向の下流側に位置している。   The exit direction is the direction of the airflow directed by the turning air passage 11, and is the downward direction in FIG. The first side plate 6 is located downstream of the second side plate 7 in the outlet direction.

図２は図１の羽根車４を示す斜視図である。図２に示す矢印は、羽根車４の回転方向である。各翼８は、羽根車４の回転方向とは反対方向に径を拡大するように傾斜している。各翼８において、羽根車４の回転方向に向いた面を圧力面８ａ、羽根車４の回転方向とは反対方向に向いた面を負圧面８ｂと呼ぶ。   FIG. 2 is a perspective view showing the impeller 4 of FIG. The arrow shown in FIG. 2 is the direction of rotation of the impeller 4. Each blade 8 is inclined so as to increase its diameter in the direction opposite to the rotation direction of the impeller 4. In each blade 8, a surface facing the rotation direction of the impeller 4 is called a pressure surface 8a, and a surface facing the direction opposite to the rotation direction of the impeller 4 is called a negative pressure surface 8b.

また、各翼８は、羽根車４の径方向の外側端部に位置する後縁８ｃを有している。後縁８ｃは、第１の側板６の外周と第２の側板７の外周とを繋ぐ翼８の縁である。なお、図１では、後縁８ｃを、子午面に回転投影した線として示している。   Each blade 8 has a trailing edge 8 c located at the radially outer end of the impeller 4. The trailing edge 8 c is an edge of the blade 8 that connects the outer periphery of the first side plate 6 and the outer periphery of the second side plate 7. In FIG. 1, the trailing edge 8c is shown as a line that is rotationally projected onto the meridian plane.

図３は実施の形態１の羽根車４の外周形状の特徴を説明するための図１の部分拡大図である。各後縁８ｃは、羽根車４の径方向の最も外側に位置する後縁先端８ｄを有している。後縁先端８ｄは、後縁８ｃ上で羽根車４の最大径となる点である。   FIG. 3 is a partially enlarged view of FIG. 1 for explaining the feature of the outer peripheral shape of the impeller 4 of the first embodiment. Each rear edge 8 c has a rear edge tip 8 d located on the outermost side in the radial direction of the impeller 4. The trailing edge tip 8d is a point that becomes the maximum diameter of the impeller 4 on the trailing edge 8c.

また、各後縁８ｃの形状は滑らかな曲線であり、各後縁８ｃは、第１の側板６に隣接する部分８ｆ及び第２の側板７に隣接する部分８ｅから後縁先端８ｄへ向けて突出量が連続して大きくなるように、羽根車４の径方向外側へ突出している。 The shape of the trailing edge 8c is a smooth curve, the trailing edge 8c is to first adjacent side plate 6 portion 8 f and a second adjacent to the side plate 7 parts 8 e from the trailing edge tip 8d Projecting outward in the radial direction of the impeller 4 so that the protruding amount continuously increases.

さらに、各後縁先端８ｄの軸方向位置は、第２の側板７の外周の軸方向位置よりも第１の側板６の外周の軸方向位置に近い。即ち、各後縁先端８ｄの軸方向位置は、第１の側板６の外周の軸方向位置と第２の側板７の外周の軸方向位置との中央（図３の直線Ｌ１）よりも出口方向の下流側である。   Further, the axial position of each trailing edge tip 8 d is closer to the axial position of the outer periphery of the first side plate 6 than the axial position of the outer periphery of the second side plate 7. That is, the axial position of each trailing edge tip 8d is in the exit direction from the center (straight line L1 in FIG. 3) between the axial position of the outer periphery of the first side plate 6 and the axial position of the outer periphery of the second side plate 7. On the downstream side.

第１の側板６の外周径（図３のＲ１）は、第２の側板７の外周径（図３のＲ２）よりも大きい。即ち、第１の側板６の外周は、第２の側板７の外周よりも羽根車の径方向の外側に位置している。   The outer peripheral diameter of the first side plate 6 (R1 in FIG. 3) is larger than the outer peripheral diameter of the second side plate 7 (R2 in FIG. 3). That is, the outer periphery of the first side plate 6 is located on the outer side in the radial direction of the impeller than the outer periphery of the second side plate 7.

図４は実施の形態１の羽根車４と転向風路１１との関係、及び転向風路１１の形状の特徴を説明するための図１の部分拡大図である。転向風路１１は、羽根車４の径方向外側に位置する転向部１１ａと、転向部１１ａの下流に位置し出口方向に沿って気流を導く排出ダクト部１１ｂとを有している。排出ダクト部１１ｂの下流側端部には、吹出口１１ｃが設けられている。   FIG. 4 is a partially enlarged view of FIG. 1 for explaining the relationship between the impeller 4 and the turning air passage 11 and the shape of the turning air passage 11 according to the first embodiment. The turning air passage 11 has a turning portion 11a located on the radially outer side of the impeller 4 and a discharge duct portion 11b that is located downstream of the turning portion 11a and guides the airflow along the outlet direction. An outlet 11c is provided at the downstream end of the discharge duct portion 11b.

排出ダクト部１１ｂは、内側フレーム円筒部９ａと形成部材１０との間に形成された風路である。また、排出ダクト部１１ｂの回転軸５に直交する断面形状は、リング状である。   The discharge duct portion 11 b is an air passage formed between the inner frame cylindrical portion 9 a and the forming member 10. Moreover, the cross-sectional shape orthogonal to the rotating shaft 5 of the discharge duct part 11b is a ring shape.

後縁先端８ｄは、第１の側板６の外周よりも羽根車４の径方向外側に位置している。即ち、後縁８ｃ上での羽根車４の最大径は、第１の側板６の外周径よりも大きい。   The trailing edge tip 8 d is located on the radially outer side of the impeller 4 with respect to the outer periphery of the first side plate 6. That is, the maximum diameter of the impeller 4 on the rear edge 8 c is larger than the outer peripheral diameter of the first side plate 6.

また、羽根車４の回転時の後縁先端８ｄの軌跡の径、即ち後縁８ｃ上での羽根車４の最大径は、転向部１１ａと排出ダクト部１１ｂとの接続面１２における排出ダクト部１１ｂの内径よりも大きく外径よりも小さい。   Further, the diameter of the locus of the trailing edge tip 8d when the impeller 4 rotates, that is, the maximum diameter of the impeller 4 on the trailing edge 8c is the discharge duct portion on the connection surface 12 between the turning portion 11a and the discharge duct portion 11b. It is larger than the inner diameter of 11b and smaller than the outer diameter.

図４において、第１の側板６の外周径をＲ１、転向部１１ａと排出ダクト部１１ｂとの接続面１２における排出ダクト部１１ｂの内径をＲ３、外径をＲ４、後縁８ｃ上での羽根車４の最大径をＲＰとすると、Ｒ１＜ＲＰ、かつ、Ｒ３＜ＲＰ＜Ｒ４となっている。   In FIG. 4, the outer peripheral diameter of the first side plate 6 is R1, the inner diameter of the discharge duct portion 11b at the connecting surface 12 between the turning portion 11a and the discharge duct portion 11b is R3, the outer diameter is R4, and the blade on the trailing edge 8c. If the maximum diameter of the vehicle 4 is RP, R1 <RP and R3 <RP <R4.

転向部１１ａは、出口方向の下流側が広く、上流側が狭くなっている。即ち、第１の側板６の外周と軸方向位置が同じ位置における形成部材１０の内径（図４の点Ｑ１の径方向寸法Ｒ５）は、第２の側板７の外周と軸方向位置が同じ位置における形成部材１０の内径（図４の点Ｑ２の径方向寸法Ｒ６）よりも大きい（Ｒ５＞Ｒ６）。このように、転向部１１ａの内壁面は、出口方向の下流側へ向けて内径が大きくなるように傾斜している。   The turning portion 11a is wide on the downstream side in the exit direction and narrow on the upstream side. That is, the inner diameter of the forming member 10 at the same position as the outer periphery of the first side plate 6 (the radial dimension R5 at the point Q1 in FIG. 4) is the same position as the outer periphery of the second side plate 7 and the axial position. Is larger than the inner diameter of the forming member 10 (the radial dimension R6 at the point Q2 in FIG. 4) (R5> R6). Thus, the inner wall surface of the turning portion 11a is inclined so that the inner diameter increases toward the downstream side in the exit direction.

排出ダクト部１１ｂには、羽根車４から流出して排出ダクト部１１ｂに流入した気流の旋回速度成分を減少させて静圧回復を行う複数の静翼１３が周方向に互いに間隔をおいて配置されている。   In the discharge duct portion 11b, a plurality of stationary blades 13 that recover the static pressure by reducing the swirl velocity component of the airflow that flows out from the impeller 4 and flows into the discharge duct portion 11b are arranged at intervals in the circumferential direction. Has been.

次に、動作について説明する。羽根車４は、モータ１の作用により出力軸３とともに回転する。羽根車４内の空気は翼８の圧力面８ａに押されて、羽根車４の径方向外側へ向かう。これにより、羽根車４の中央部では圧力が低くなり、吸込口７ａから羽根車４内に外気が供給される。   Next, the operation will be described. The impeller 4 rotates together with the output shaft 3 by the action of the motor 1. The air in the impeller 4 is pushed by the pressure surface 8 a of the blade 8 and travels outward in the radial direction of the impeller 4. Thereby, a pressure becomes low in the center part of the impeller 4, and external air is supplied in the impeller 4 from the suction inlet 7a.

径方向外側へ向かった羽根車４内の空気は、第１の側板６の外周と第２の側板７の外周と翼８の後縁８ｃとで構成される羽根車４の流出口から羽根車４外へ流出し、転向風路１１の転向部１１ａに流入する。   The air in the impeller 4 facing radially outward is impeller from the outlet of the impeller 4 constituted by the outer periphery of the first side plate 6, the outer periphery of the second side plate 7, and the trailing edge 8 c of the blade 8. 4 flows out and flows into the turning portion 11 a of the turning air passage 11.

羽根車４から流出した空気は、転向部１１ａにおいて出口方向へ急激に向きを変えられる。出口方向へ向きを変えられた空気は、排出ダクト部１１ｂを通過して吹出口１１ｃから外部へ放出される。   The air that has flowed out of the impeller 4 is suddenly changed in the direction of the exit at the turning portion 11a. The air whose direction is changed in the outlet direction passes through the discharge duct portion 11b and is discharged to the outside from the blower outlet 11c.

転向部１１ａにおいて、気流の径方向成分を軸方向へ曲げる際に生じる損失を小さくするには、転向風路１１の径方向寸法を大きくして、曲がりの曲率半径を大きくすればよい。しかし、その場合には、送風機全体の寸法が大きくなってしまうため、送風機寸法に制約がある場合にはこの方法は選択できない。また、羽根車４の径を小さくすると、必要な仕事率が得られなくなってしまう。   In the turning portion 11a, in order to reduce the loss that occurs when the radial component of the airflow is bent in the axial direction, the radial dimension of the turning air passage 11 may be increased to increase the curvature radius of the bending. However, in that case, since the size of the entire blower is increased, this method cannot be selected when the size of the blower is limited. Moreover, if the diameter of the impeller 4 is made small, a required work rate cannot be obtained.

これに対して、実施の形態１の遠心送風機では、上記のような構成としたことにより、限られた径方向寸法において羽根車４からの流出気流が軸方向へ向きを変えるときの曲がり損失を小さくすることができ、必要な仕事率に対して入力を小さくすることができる。   On the other hand, in the centrifugal blower of the first embodiment, the above-described configuration reduces the bending loss when the outflow airflow from the impeller 4 changes in the axial direction in a limited radial dimension. The input can be reduced with respect to the required power.

以下、実施の形態１の遠心送風機の翼８の後縁８ｃ付近における空気の動作の詳細を説明する。実施の形態１の遠心送風機では、後縁先端８ｄの軸方向位置は、第２の側板７の外周の軸方向位置よりも第１の側板６の外周の軸方向位置に近い。また、後縁８ｃは、第２の側板７に隣接する部分８ｅから後縁先端８ｄへ向けて羽根車４の径方向外側へ突出している。さらに、翼８の負圧面８ｂ側は、圧力が低く周囲から空気を吸引する。 Hereinafter, details of the operation of air in the vicinity of the trailing edge 8c of the blade 8 of the centrifugal blower of the first embodiment will be described. In the centrifugal blower of the first embodiment, the axial position of the trailing edge tip 8 d is closer to the axial position of the outer periphery of the first side plate 6 than the axial position of the outer periphery of the second side plate 7. Further, the rear edge 8 c protrudes outward in the radial direction of the impeller 4 from the portion 8 e adjacent to the second side plate 7 toward the rear edge tip 8 d. Further, the suction surface 8b side of the blade 8 has a low pressure and sucks air from the surroundings.

翼８が空気に作用する力は、周速が高いほど大きくなるので、軸方向位置が第２の側板７の外周よりも第１の側板６に近い位置で最も大きな吸引力を生じることになる。このため、後縁８ｃ近傍の空気に対して、第２の側板７側から出口方向への力が与えられる。これにより、転向部１１ａの内壁への衝突にともなう圧力上昇が小さくなり、曲がり損失が小さくなる。よって、羽根車４の径方向外側における転向にともなう損失を小さくし、必要な仕事率に対して入力の小さい高効率な遠心送風機を得ることができる。   Since the force that the blade 8 acts on the air increases as the peripheral speed increases, the largest suction force is generated at a position where the axial position is closer to the first side plate 6 than the outer periphery of the second side plate 7. . For this reason, force in the direction of the exit from the second side plate 7 side is applied to the air in the vicinity of the rear edge 8c. Thereby, the pressure rise accompanying the collision with the inner wall of the turning part 11a becomes small, and bending loss becomes small. Therefore, the loss accompanying the turning of the impeller 4 on the radially outer side can be reduced, and a highly efficient centrifugal fan having a small input with respect to the required power can be obtained.

また、実施の形態１の遠心送風機では、後縁先端８ｄが第１の側板６の外周よりも羽根車４の径方向外側に位置している。また、後縁８ｃ上での羽根車４の最大径が、転向部１１ａと排出ダクト部１１ｂとの接続面１２における排出ダクト部１１ｂの内径よりも大きく外径よりも小さい。   Further, in the centrifugal blower of the first embodiment, the trailing edge tip 8 d is located on the radially outer side of the impeller 4 with respect to the outer periphery of the first side plate 6. Further, the maximum diameter of the impeller 4 on the rear edge 8c is larger than the inner diameter of the discharge duct portion 11b on the connection surface 12 between the turning portion 11a and the discharge duct portion 11b and smaller than the outer diameter.

このため、後縁８ｃの第１の側板６から後縁先端８ｄまで部分は、軸方向において出口方向に向いた形状となり、転向部１１ａと排出ダクト部１１ｂとの接続面１２と対向する。これにより、後縁８ｃの第１の側板６から後縁先端８ｄまで部分が成す回転面から、接続面１２に向かって空気を流出させることができるようになり、曲がり損失をさらに小さくすることができる。よって、さらに高効率な遠心送風機を得ることができる。   Therefore, the portion of the rear edge 8c from the first side plate 6 to the rear edge tip 8d has a shape facing the outlet direction in the axial direction, and faces the connection surface 12 between the turning portion 11a and the discharge duct portion 11b. As a result, air can flow out from the rotating surface formed by the portion of the rear edge 8c from the first side plate 6 to the rear edge tip 8d toward the connection surface 12, and the bending loss can be further reduced. it can. Therefore, a further highly efficient centrifugal fan can be obtained.

さらに、実施の形態１の遠心送風機では、第１の側板６の外周径が第２の側板７の外周径よりも大きい。このため、羽根車４の径方向の第２の側板７の外周から第１の側板６の外周までの領域において、第１の側板６側は翼８が存在し負圧面８ｂによる吸引力が相対的に大きい。一方、第２の側板７側は翼８が部分的に存在するか又は存在しない形状となり、負圧面８ｂによる吸引力が相対的に小さい。   Furthermore, in the centrifugal blower of the first embodiment, the outer peripheral diameter of the first side plate 6 is larger than the outer peripheral diameter of the second side plate 7. Therefore, in the region from the outer periphery of the second side plate 7 in the radial direction of the impeller 4 to the outer periphery of the first side plate 6, the first side plate 6 side has the blades 8, and the suction force by the negative pressure surface 8 b is relatively low. It ’s big. On the other hand, the second side plate 7 side has a shape in which the blades 8 are partially present or absent, and the suction force by the suction surface 8b is relatively small.

従って、気流の出口方向への成分をより大きく得ることができ、上述した後縁８ｃ近傍の空気に対して出口方向への力を与える作用をより大きくすることができ、曲がり損失をさらに小さくすることができる。よって、さらに高効率な遠心送風機を得ることができる。   Therefore, it is possible to obtain a larger component of the airflow in the outlet direction, to increase the action of applying the force in the outlet direction to the air in the vicinity of the trailing edge 8c described above, and to further reduce the bending loss. be able to. Therefore, a further highly efficient centrifugal fan can be obtained.

ここで、羽根車４から流出する空気は、その径方向速度成分と旋回速度成分とが大きい。また、径方向速度成分による慣性力に旋回速度成分による遠心力が加わり、羽根車４から流出した空気は、転向部１１ａの内壁に押し付けられる。   Here, the air flowing out from the impeller 4 has a large radial speed component and turning speed component. Moreover, the centrifugal force by a turning speed component is added to the inertia force by a radial direction speed component, and the air which flowed out from the impeller 4 is pressed against the inner wall of the turning part 11a.

これに対して、実施の形態１の遠心送風機では、転向部１１ａの内壁が、出口側の径に対して反対側の径が相対的に小さくなるように傾斜しているため、その傾きに応じて、空気を内壁に押し付ける力の一部が、内壁に沿って排出ダクト部１１ｂへ向ける力に変えられる。   On the other hand, in the centrifugal blower of the first embodiment, the inner wall of the turning portion 11a is inclined so that the diameter on the opposite side is relatively smaller than the diameter on the outlet side. Thus, a part of the force pressing the air against the inner wall is changed to a force directed toward the discharge duct portion 11b along the inner wall.

このため、転向部１１ａの内壁への衝突にともなう圧力上昇を小さくし、曲がり損失を小さくすることができる。よって、さらに高効率な遠心送風機を得ることができる。   For this reason, the pressure rise accompanying the collision with the inner wall of the turning part 11a can be made small, and bending loss can be made small. Therefore, a further highly efficient centrifugal fan can be obtained.

さらに、実施の形態１の遠心送風機では、排出ダクト部１１ｂの接続面１２から吹出口１１ｃまでの間に、静翼１３が設けられている。このため、昇圧能力が高まり、必要昇圧能力に対して羽根車４での昇圧割合を低くすることができ、羽根車４の入力を低くすることができる。また、静翼１３は、軸方向で羽根車４と重ならないので、静翼１３を設置しても羽根車４の径を縮小する必要がない。このため、限られた径方向寸法に対して高い出力の遠心送風機とすることができる。   Furthermore, in the centrifugal blower of the first embodiment, the stationary blade 13 is provided between the connection surface 12 of the discharge duct portion 11b and the outlet 11c. For this reason, the boosting capability is increased, the rate of boosting at the impeller 4 can be lowered relative to the required boosting capability, and the input of the impeller 4 can be lowered. Further, since the stationary blade 13 does not overlap the impeller 4 in the axial direction, it is not necessary to reduce the diameter of the impeller 4 even if the stationary blade 13 is installed. For this reason, it can be set as the high output centrifugal fan with respect to the limited radial direction dimension.

図５は実施の形態１の遠心送風機を内蔵した電気掃除機を示す構成図である。掃除機本体２１には、実施の形態１と同様の遠心送風機２２と、集塵ボックス２３とが収容されている。また、掃除機本体２１には、屈曲自在のホース２４を介して棒状のパイプ２５が接続されている。パイプ２５のホース２４とは反対側の端部には、ヘッド部２６が接続されている。   FIG. 5 is a configuration diagram showing the electric vacuum cleaner incorporating the centrifugal blower of the first embodiment. The vacuum cleaner main body 21 accommodates a centrifugal blower 22 and a dust collection box 23 similar to those in the first embodiment. In addition, a rod-like pipe 25 is connected to the cleaner body 21 via a bendable hose 24. A head portion 26 is connected to the end of the pipe 25 opposite to the hose 24.

遠心送風機２２のモータ１を駆動して気流を発生させることにより、ヘッド部２６の吸引口から空気とともに塵埃が吸引される。吸引された空気及び塵埃は、パイプ２５及びホース２４を通して掃除機本体２１内に送られる。そして、塵埃は集塵ボックス２３内に溜められ、空気は遠心送風機２２を通して掃除機本体２１外へ排出される。   By driving the motor 1 of the centrifugal blower 22 to generate an air flow, dust is sucked together with air from the suction port of the head portion 26. The sucked air and dust are sent into the cleaner body 21 through the pipe 25 and the hose 24. The dust is stored in the dust collection box 23, and the air is discharged out of the cleaner body 21 through the centrifugal blower 22.

上記のような遠心送風機２２を用いることにより、電気掃除機の高出力化、高効率化及び小型化を実現することができる。   By using the centrifugal blower 22 as described above, high output, high efficiency, and miniaturization of the vacuum cleaner can be realized.

なお、上記の例では、空気を送る遠心送風機を示したが、空気以外の気体を送るものであってもよい。
また、後縁先端８ｄの軸方向位置は、第１の側板６の外周の軸方向位置と同じであってもよい。
さらに、この発明の遠心送風機は、電気掃除機以外にも適用することができる。In the above example, the centrifugal blower for sending air is shown, but a gas other than air may be sent.
Further, the axial position of the trailing edge tip 8 d may be the same as the axial position of the outer periphery of the first side plate 6.
Furthermore, the centrifugal blower of the present invention can be applied to other than vacuum cleaners.

１ モータ、４ 羽根車、６ 第１の側板、７ 第２の側板、８ 翼、８ｃ 後縁、８ｄ 後縁先端、１０ 形成部材、１１ 転向風路、１１ａ 転向部、１１ｂ 排出ダクト部、１３ 静翼、２２ 遠心送風機。   DESCRIPTION OF SYMBOLS 1 Motor, 4 impeller, 6 1st side plate, 7 2nd side plate, 8 wing | blade, 8c Trailing edge, 8d Trailing edge tip, 10 Forming member, 11 Turning air path, 11a Turning part, 11b Exhaust duct part, 13 Static blade, 22 Centrifugal blower.

Claims (5)

モータ、
第１の側板と、前記第１の側板に対向する第２の側板と、前記第１の側板と前記第２の側板との間に保持されている複数の翼とを有しており、前記モータにより駆動される遠心型の羽根車、及び
前記羽根車の外周を覆い、前記羽根車から流出された直後の気流の方向を前記羽根車の軸方向の一側である出口方向に変えるための転向風路を形成する形成部材
を備え、
前記第１の側板は、前記第２の側板よりも出口側に位置しており、
前記翼は、前記羽根車の径方向の外側端部に位置する後縁を有しており、
前記後縁は、前記羽根車の径方向の最も外側に位置する後縁先端を有しており、かつ、前記第２の側板に隣接する部分及び前記第１の側板に隣接する部分から前記後縁先端へ向けて前記羽根車の径方向外側へ突出しており、
前記後縁先端の軸方向位置は、前記第１の側板の外周の軸方向位置と前記第２の側板の外周の軸方向位置との中央よりも前記出口側であり、
前記転向風路は、前記羽根車の径方向外側に位置する転向部と、前記転向部の下流に位置し前記出口方向に沿って気流を導く排出ダクト部とを有しており、
前記後縁先端は、前記第１の側板の外周よりも前記羽根車の径方向外側に位置しており、
前記羽根車の回転時の前記後縁先端の軌跡の径は、前記転向部と前記排出ダクト部との接続面における前記排出ダクト部の内径よりも大きく外径よりも小さい遠心送風機。 motor,
A first side plate, a second side plate facing the first side plate, and a plurality of wings held between the first side plate and the second side plate, A centrifugal impeller driven by a motor, and an outer periphery of the impeller for changing the direction of the airflow immediately after flowing out of the impeller to an exit direction which is one side in the axial direction of the impeller A forming member for forming a turning air passage,
The first side plate is located on the outlet side of the second side plate,
The blade has a trailing edge located at a radially outer end of the impeller;
The rear edge has a rear edge tip located on the outermost side in the radial direction of the impeller, and the rear edge from the portion adjacent to the second side plate and the portion adjacent to the first side plate. Projecting radially outward of the impeller toward the edge tip,
The axial position of the trailing edge tip, Ri said outlet der than the center of the axial position of the outer periphery of said first side plate axial position and said second side plate of the outer periphery of,
The turning air passage has a turning portion located on the radially outer side of the impeller, and a discharge duct portion that is located downstream of the turning portion and guides an air flow along the outlet direction,
The trailing edge tip is located radially outside the impeller from the outer periphery of the first side plate,
The diameter of the locus | trajectory of the said trailing edge tip at the time of rotation of the said impeller is larger than the internal diameter of the said discharge duct part in the connection surface of the said turning part and the said discharge duct part, and is smaller than an outer diameter . 前記転向部の内壁面は、前記出口側へ向けて内径が大きくなるように傾斜している請求項１記載の遠心送風機。 It said inner wall surface of the turning section, a centrifugal blower according to claim 1, wherein the inclined such inner diameter increases toward the exit side. 前記排出ダクト部には、気流の旋回速度成分を減少させて静圧回復を行う静翼が配置されている請求項１又は請求項２に記載の遠心送風機。 The centrifugal blower according to claim 1 or 2 , wherein a stationary blade that recovers a static pressure by reducing a swirl velocity component of the airflow is disposed in the discharge duct portion. 前記第１の側板の外周径は、前記第２の側板の外周径よりも大きい請求項１から請求項３までのいずれか１項に記載の遠心送風機。 The centrifugal blower according to any one of claims 1 to 3 , wherein an outer peripheral diameter of the first side plate is larger than an outer peripheral diameter of the second side plate. 請求項１から請求項４までのいずれか１項に記載の遠心送風機を備えている電気掃除機。 The vacuum cleaner provided with the centrifugal air blower of any one of Claim 1- Claim 4 .
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AU2014393558B2 (en) 2017-09-07
CN106460867A (en) 2017-02-22
AU2014393558A1 (en) 2016-11-03
CN106460867B (en) 2018-09-25
TWI573551B (en) 2017-03-11
TW201542155A (en) 2015-11-16
WO2015170401A1 (en) 2015-11-12

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