JP2008121589A - Electric blower and vacuum cleaner using the electric blower - Google Patents

Electric blower and vacuum cleaner using the electric blower Download PDF

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JP2008121589A
JP2008121589A JP2006307424A JP2006307424A JP2008121589A JP 2008121589 A JP2008121589 A JP 2008121589A JP 2006307424 A JP2006307424 A JP 2006307424A JP 2006307424 A JP2006307424 A JP 2006307424A JP 2008121589 A JP2008121589 A JP 2008121589A
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Prior art keywords
impeller
inlet
electric blower
cross
hub
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JP2006307424A
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JP2008121589A5 (en
JP4867596B2 (en
Inventor
Hiroyuki Kayama
博之 香山
Kazushige Nakamura
一繁 中村
Shizuka Yokote
静 横手
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Panasonic Holdings Corp
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Matsushita Electric Industrial Co Ltd
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Priority to JP2006307424A priority Critical patent/JP4867596B2/en
Priority to CNU2007201396980U priority patent/CN201037473Y/en
Priority to CNB2007100967749A priority patent/CN100516546C/en
Priority to EP07012832.7A priority patent/EP1923572B1/en
Priority to KR1020070066813A priority patent/KR101287250B1/en
Publication of JP2008121589A publication Critical patent/JP2008121589A/en
Publication of JP2008121589A5 publication Critical patent/JP2008121589A5/ja
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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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • 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
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
    • F04D25/082—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation the unit having provision for cooling the motor
    • 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
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5806—Cooling the drive system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/70—Shape

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

Abstract

<P>PROBLEM TO BE SOLVED: To provide an electric blower for sufficiently improving impeller air blowing efficiency. <P>SOLUTION: A flow passage cross-sectional area change is continuously expanded up to an outlet 25 from an inlet 5 including a diffuser 8 of an impeller 1. Thus, a flow speed caused by a flow rate inside of the impeller 1, is continuously gradually decelerated over the whole flow passage area up to the outlet 25 from the inlet 5. Air blowing efficiency is sufficiently improved since acceleration and sudden deceleration are not repeated. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

本発明は、インペラ送風効率向上を図った電動送風機およびこれを用いた電気掃除機に関するものである。   The present invention relates to an electric blower that improves impeller blowing efficiency and a vacuum cleaner using the electric blower.

従来、この種のインペラ送風効率向上を図った電動送風機はすでに提案されている（例えば、特許文献１参照）。   Conventionally, an electric blower that has improved the impeller blowing efficiency of this type has already been proposed (see, for example, Patent Document 1).

これは、図１０に示すように、インペラ４０が、前面シュラウド４１、後面シュラウド４２および両シュラウド間の複数枚のブレード４３により構成されている。そして、前面シュラウド４１の形状は、前面シュラウド４１から後面シュラウド（基板）４２までの距離が中心から外周にいく程短くなるように（ａ＞ｂ＞ｃ＞ｄ）前面シュラウド４１を傾斜させ、かつ、前面シュラウド４１の径方向の断面形状を曲線形状としている。これにより、図１１（ａ）に示すように、インペラ４０の内径から外径にかけて（流路入口から流路出口にかけて）径方向における流路の円筒断面積変化が直線的に増加し、図１１（ｂ）に示すように、流路入口から流路出口にかけて径方向の流速の変化が直線状に減少するものである。
特開２００６−９６６９号公報 As shown in FIG. 10, the impeller 40 includes a front shroud 41, a rear shroud 42, and a plurality of blades 43 between the shrouds. The shape of the front shroud 41 is such that the front shroud 41 is inclined so that the distance from the front shroud 41 to the rear shroud (substrate) 42 decreases from the center to the outer periphery (a>b>c> d), and The cross-sectional shape in the radial direction of the front shroud 41 is a curved shape. As a result, as shown in FIG. 11A, the change in the cylindrical cross-sectional area of the flow path in the radial direction increases linearly from the inner diameter to the outer diameter of the impeller 40 (from the flow path inlet to the flow path outlet). As shown in (b), the change in the flow velocity in the radial direction decreases linearly from the channel inlet to the channel outlet.
JP 2006-9669 A

しかしながら、前記従来の構成では、吸引した気流が回転軸方向から径方向に曲がるインペラ４０（特に、ハブと入口案内翼とを有するインデューサを配したインペラ）の入口部では前面シュラウド４１と後面シュラウド４２の距離変化と、前面シュラウド４１の曲線形状だけでは十分なインペラ送風効率向上を図る流路断面積を構成することができないという課題を有していた。   However, in the conventional configuration, the front shroud 41 and the rear shroud are provided at the inlet portion of the impeller 40 (in particular, the impeller provided with an inducer having a hub and inlet guide vanes) in which the sucked airflow is bent in the radial direction from the rotation axis direction. Only the change in the distance of 42 and the curved shape of the front shroud 41 have a problem that the flow passage cross-sectional area for improving the impeller blowing efficiency cannot be configured sufficiently.

本発明は、前記従来の課題を解決するもので、十分なインペラ送風効率向上を図った電動送風機およびこれを用いた電気掃除機を提供することを目的とする。   This invention solves the said conventional subject, and it aims at providing the electric blower which aimed at sufficient impeller ventilation efficiency improvement, and a vacuum cleaner using the same.

前記従来の課題を解決するために、本発明の電動送風機は、インペラのインデューサを含めた入口から出口までの流路断面積変化を拡大させたものである。   In order to solve the above-mentioned conventional problems, the electric blower of the present invention expands the change in the flow passage cross-sectional area from the inlet to the outlet including the impeller inducer.

これによって、インペラ内部の流量に起因する流速が入口から出口までの全流路領域に渡って徐々に減速していき、加速や急減速を繰り返さないため、十分な送風効率の向上が図れるものである。   As a result, the flow velocity caused by the flow rate inside the impeller gradually decelerates over the entire flow path region from the inlet to the outlet, and acceleration and sudden deceleration are not repeated, so that sufficient ventilation efficiency can be improved. is there.

また、この電動送風機を用いた電気掃除機は、吸引性能が高く、快適な掃除ができるものである。   Moreover, the vacuum cleaner using this electric blower has high suction performance and can perform comfortable cleaning.

本発明の電動送風機およびこれを用いた電気掃除機は、十分な送風効率の向上が図れるものである。   The electric blower of the present invention and the electric vacuum cleaner using the electric blower can sufficiently improve the blowing efficiency.

第１の発明は、前面シュラウド、後面シュラウドおよび両シュラウド間の複数枚のブレードとを有するインペラと、前記インペラの入口内部に配した山型のハブおよび入口案内翼とを有するインデューサと、前記インペラの外周に位置した複数枚の静翼およびその基板とを有するエアガイドと、前記エアガイドとともにインペラを内包し中央に吸気孔を有したケーシングと、前記インペラを回転駆動させる電動機とを備え、前記インペラのインデューサを含めた入口から出口までの流路断面積変化を拡大させた電動送風機とすることにより、インペラ内部の流量に起因する流速が入口から出口までの全流路領域に渡って徐々に減速していき、加速や急減速を繰り返さないため、十分な送風効率の向上が図れるものである。   A first invention includes an impeller having a front shroud, a rear shroud, and a plurality of blades between the shrouds, a mountain-shaped hub and an inlet guide vane arranged inside the inlet of the impeller, An air guide having a plurality of stationary blades and its substrate positioned on the outer periphery of the impeller, a casing including the impeller together with the air guide and having an air intake hole in the center, and an electric motor for rotationally driving the impeller, By using an electric blower that expands the cross-sectional area change from the inlet to the outlet including the impeller inducer, the flow velocity caused by the flow rate inside the impeller extends over the entire flow path region from the inlet to the outlet. Since the vehicle gradually decelerates and does not repeat acceleration and rapid deceleration, the air blowing efficiency can be sufficiently improved.

第２の発明は、特に、第１の発明において、流路断面積変化は、略直線状であることにより、インペラ内部の流量に起因する成分の流速が、回転軸断面の流れ方向に対して一定の割合で減速していくことで急減速を発生させないものである。   In the second invention, in particular, in the first invention, the flow passage cross-sectional area change is substantially linear, so that the flow velocity of the component caused by the flow rate inside the impeller is relative to the flow direction of the rotary shaft cross section. By decelerating at a constant rate, sudden deceleration is not generated.

第３の発明は、特に、第１または第２の発明において、流路断面積変化は、インペラの入口からハブ終端部と、ハブ終端部から出口とで異なることにより、入口からハブ終端部までと、ハブ終端部から出口までを分離して設計することができ、入口側では吸引された流れが回転軸方向から径方向へ変る際に生じる剥離や渦、２次流れなどによる損失を低減する流路断面積変化を構成し、また出口側では径方向に排出するまでに生じる剥離や渦、円板回転摩擦損失などによる損失を低減する流路断面積変化を構成し、送風効率の向上を図れるものである。   According to a third aspect of the invention, in particular, in the first or second aspect of the present invention, the change in the cross-sectional area of the flow path is different from the inlet of the impeller to the hub end portion and from the hub end portion to the outlet. And can be designed separately from the hub end to the outlet, reducing the loss due to separation, vortex, secondary flow, etc. that occur when the suctioned flow changes from the rotation axis direction to the radial direction on the inlet side The flow cross-sectional area change is configured, and on the outlet side, the flow cross-sectional area change is reduced to reduce the loss due to separation, vortex, disc rotational friction loss, etc. that occurs before discharging in the radial direction, improving the blowing efficiency It can be planned.

第４の発明は、特に、第３の発明において、インペラの入口からハブ終端部までの流路断面積変化が、ハブ終端部から出口までの流路断面積変化に比べて変化率が大きい構成としたことにより、吸引された流れが回転軸方向から径方向へ変る際に生じる剥離や渦、２次流れで実際に空気が流れる面積が狭くなる場合に、流路断面積変化を略直線状に近付けることができ、インペラ内部の流量に起因する成分の流速が、回転軸断面の流れ方向に対して一定の割合で減速していくことで急減速を発生させないものである。   In the fourth aspect of the invention, in particular, in the third aspect of the invention, the change in the flow passage cross-sectional area from the impeller inlet to the hub end is larger than the change in the flow cross-sectional area from the hub end to the outlet. As a result, separation or vortex generated when the suctioned flow changes from the rotation axis direction to the radial direction, and when the area where the air actually flows in the secondary flow becomes narrower, the change in the cross-sectional area of the flow path is substantially linear. The flow velocity of the component due to the flow rate inside the impeller is decelerated at a constant rate with respect to the flow direction of the rotary shaft cross section, so that rapid deceleration is not generated.

第５の発明は、特に、第１の発明において、流路断面積変化は、インペラの入口からハブ終端部と、ハブ終端部から出口とで異なり、かつそれぞれが略直線状であり、さらにハブ終端部近傍には入口側と出口側の流路断面積変化を接続する曲線変化部を有することにより、インペラの入口部からハブ終端部、そしてハブ終端部から出口へと円滑に流路断面積を変化させ、つまり流量に起因する成分の流速を滑らかに減速させることができる。   According to a fifth aspect of the present invention, in the first aspect of the invention, the flow path cross-sectional area changes from the inlet of the impeller to the end of the hub and from the end of the hub to the outlet, and each is substantially linear. In the vicinity of the terminal end, there is a curve changing part that connects the change in the channel cross-sectional area of the inlet side and the outlet side, so that the cross-sectional area of the flow path smoothly from the impeller inlet to the hub terminal and from the hub terminal to the outlet. , That is, the flow velocity of the component due to the flow rate can be smoothly decelerated.

第６の発明は、特に、第１〜第５のいずれか１つの発明において、インペラは、前面シュラウドおよびハブの入口部に回転軸方向と平行な平行部を有することにより、インペラ入口で回転軸方向に吸引させて、全ての回転軸方向の流れを径方向の流れに円滑に変化させることができる。   According to a sixth aspect of the invention, in particular, in any one of the first to fifth aspects of the invention, the impeller includes a parallel portion parallel to the rotational axis direction at the inlet portion of the front shroud and the hub, so that the rotational shaft at the impeller inlet. By sucking in the direction, it is possible to smoothly change the flow in the direction of the rotation axis to the flow in the radial direction.

第７の発明は、特に、第１〜第６のいずれか１つの発明において、インデューサを樹脂製とし、前面シュラウド、後面シュラウドおよびブレードを板金製としたことにより、材質および製造方法の異なるインペラ入口側であるインデューサ部の流路と、出口側である板金部の流路（前面シュラウドと後面シュラウドで挟まれた流路）を個別に製作することができ、簡易にインペラを構成することができる。   According to a seventh invention, in particular, in any one of the first to sixth inventions, the inducer is made of resin, and the front shroud, the rear shroud, and the blade are made of sheet metal. The flow path of the inducer section on the inlet side and the flow path of the sheet metal section on the outlet side (flow path sandwiched between the front shroud and the rear shroud) can be individually manufactured, and the impeller can be configured easily. Can do.

第８の発明は、特に、第１〜第７のいずれか１つの発明における電動送風機を有する電気掃除機としたことにより、吸引性能が高く、快適な掃除ができる。   In particular, the eighth aspect of the invention is a vacuum cleaner having the electric blower according to any one of the first to seventh aspects of the invention, so that the suction performance is high and comfortable cleaning can be performed.

以下、本発明の実施の形態について、図面を参照しながら説明する。なお、この実施の形態によって本発明が限定されるものではない。   Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.

（実施の形態１）
図１〜図４は、本発明の実施の形態１における電動送風機を示している。 (Embodiment 1)
1 to 4 show an electric blower according to Embodiment 1 of the present invention.

図１、図２に示すように、本実施の形態における電動送風機は、前面シュラウド２、後面シュラウド３および両シュラウド２、３間の複数枚のブレード４を有するインペラ１と、インペラ１の入口５内部に配した円錐状で山型のハブ６および３次元的曲面を有しブレード４に接続された入口案内翼７を有するインデューサ８と、インペラ１の外周に位置した複数枚の静翼９およびその基板１０とを有するエアガイド１１と、エアガイド１１とともにインペラ１を内包し中央に入口５と対向する吸気孔１２を有したケーシング１３と、インペラ１を回転駆動させる電動機１４とを備えている。   As shown in FIGS. 1 and 2, the electric blower in the present embodiment includes an impeller 1 having a front shroud 2, a rear shroud 3, and a plurality of blades 4 between the shrouds 2 and 3, and an inlet 5 of the impeller 1. A conical and mountain-shaped hub 6 disposed inside, an inducer 8 having an inlet guide blade 7 having a three-dimensional curved surface and connected to the blade 4, and a plurality of stationary blades 9 positioned on the outer periphery of the impeller 1. And an air guide 11 having the substrate 10, a casing 13 containing the impeller 1 together with the air guide 11 and having an intake hole 12 facing the inlet 5 in the center, and an electric motor 14 for rotating the impeller 1. Yes.

そして、インペラ１のインデューサ８を含めた入口５から出口２５までの流路断面積変化を連続して拡大させた構成としている。   And the flow-path cross-sectional area change from the inlet 5 including the inducer 8 of the impeller 1 to the exit 25 is set as the structure expanded continuously.

また、インペラ１を構成する前面シュラウド２、後面シュラウド３および複数枚のブレード４は、本実施の形態では、いずれも板金製であり、これら三部品はかしめ加工などにより締結されている。また、インデューサ８は樹脂製であり、板金製の三部品（前面シュラウド２、後面シュラウド３、ブレード４）を締結する際に内部に挿入し共締めされている。インデューサ８はそのハブ終端部２６においてインペラ１と接続され、入口案内翼７が各ブレード４に接続されている。   Further, the front shroud 2, the rear shroud 3, and the plurality of blades 4 constituting the impeller 1 are all made of sheet metal in the present embodiment, and these three parts are fastened by caulking or the like. The inducer 8 is made of resin, and is inserted into the inside and fastened together when three parts made of sheet metal (front shroud 2, rear shroud 3, and blade 4) are fastened. The inducer 8 is connected to the impeller 1 at the hub end portion 26, and the inlet guide vane 7 is connected to each blade 4.

また、インペラ１は、後面シュラウド３およびハブ６内のボス１５が電動機１４の回転軸１６に座金１７を介してナット１８にて固着されている。   In the impeller 1, a rear shroud 3 and a boss 15 in the hub 6 are fixed to a rotating shaft 16 of an electric motor 14 with a nut 18 via a washer 17.

このインペラ１において、前面シュラウド２および後面シュラウド３を含むハブ６側の回転軸１６方向の断面形状（子午面形状）は、図３に示すような構成としている。   In the impeller 1, the cross-sectional shape (meridional surface shape) in the direction of the rotating shaft 16 on the hub 6 side including the front shroud 2 and the rear shroud 3 is configured as shown in FIG.

すなわち、前面シュラウド２の回転軸１６方向の断面を取った時の流路側の前面側曲線１９と、同じくハブ６とこのハブ６から連続した後面シュラウド３からなる流路側の後面側曲線２０とに挟まれ、これら２つの曲線（前面側曲線１９、後面側曲線２０）の略中央を通る流路中心曲線２１に垂直な多数の流路断面定義直線２２を求め、この流路断面定義直線２２を通り回転軸１６周りに回転させた円環状の曲面をそれぞれの箇所における流路断面積とする。   That is, the front side curve 19 on the flow path side when the cross section of the front shroud 2 in the direction of the rotation axis 16 is taken, and the rear side curve 20 on the flow path side composed of the hub 6 and the rear shroud 3 continuous from the hub 6. A large number of flow path cross-sectional definition lines 22 perpendicular to a flow path center curve 21 that are sandwiched and pass through the approximate center of these two curves (the front side curve 19 and the rear side curve 20) are obtained. An annular curved surface rotated around the rotation axis 16 is defined as a flow path cross-sectional area at each location.

このそれぞれの箇所における流路断面積がインペラ１の流路中心曲線２１上の入口５から出口２５にかけて連続して徐々に拡大させ、図４（ａ）に示すように、その変化が略直線状となるようにしている。これにより、図４（ｂ）に示すように、入口５から出口２５にかけての流速の変化が直線状に減少するものである。   The cross-sectional area of the flow path at each location is gradually and continuously enlarged from the inlet 5 to the outlet 25 on the flow path center curve 21 of the impeller 1, and the change is substantially linear as shown in FIG. It is trying to become. Thereby, as shown in FIG.4 (b), the change of the flow velocity from the inlet 5 to the outlet 25 reduces linearly.

なお、流路中心曲線２１は、前面側曲線１９と後面側曲線２０をそれぞれ同じ数だけ等分割し、それぞれ対応する分割点２３を結び、この結ばれた分割線２４の中点を通る曲線とする。   In addition, the flow path center curve 21 is obtained by dividing the front side curve 19 and the rear side curve 20 equally by the same number, connecting the corresponding dividing points 23, and passing through the middle point of the connected dividing line 24. To do.

以上のように構成された電動送風機について、以下その動作、作用を説明する。   About the electric blower comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

図１、図２において、電動機１４に接続されたインペラ１が高速回転して（矢印Ａ）、ケーシング１３の吸気孔１２から空気を吸込み（矢印Ｂ）、続いてインペラ１の入口５から空気を吸込み、この空気流は前面シュラウド２、ハブ６、そして２枚の入口案内翼７で囲まれる内部流路で回転軸１６方向から径方向へ曲げられ（矢印Ｃ）、続く前面シュラウド２、後面シュラウド３、そして２枚のブレード４で囲まれる内部流路を通過し（矢印Ｄ）、インペラ１外周部から排出される。   1 and 2, the impeller 1 connected to the electric motor 14 rotates at high speed (arrow A), sucks air from the intake hole 12 of the casing 13 (arrow B), and then draws air from the inlet 5 of the impeller 1. This air flow is bent in the radial direction from the direction of the rotating shaft 16 (arrow C) in the internal flow path surrounded by the front shroud 2, the hub 6 and the two inlet guide vanes 7 (arrow C), followed by the front shroud 2, the rear shroud 3 and passes through an internal flow path surrounded by two blades 4 (arrow D), and is discharged from the outer periphery of the impeller 1.

インペラ１から排出された空気流は、エアガイド１１の静翼９間を通過し、ケーシング１３の外周壁に衝突後（矢印Ｅ）、またエアガイド１１の裏面（矢印Ｆ）、続いて電動機１４の内部を冷却しながら通過し（矢印Ｇ）、電動機１４に設けた排気孔から電動機１４外へ排出される（矢印Ｈ）。   The air flow discharged from the impeller 1 passes between the stationary blades 9 of the air guide 11, collides with the outer peripheral wall of the casing 13 (arrow E), the back surface of the air guide 11 (arrow F), and then the electric motor 14. Is passed through while cooling (arrow G), and is discharged out of the motor 14 through an exhaust hole provided in the motor 14 (arrow H).

そのとき、インペラ１のインデューサ８を含めた入口５から出口２５までの流路断面積変化が拡大方向のみである流路形状を持つハブ６形状、前面シュラウド２形状、後面シュラウド３形状とすることにより、インペラ１内部の流量に起因する成分（回転軸１６断面方向の成分）の流速が入口５から出口２５までの全流路領域に渡って連続して徐々に減速していき（図４（ｂ））、加速や急減速を繰り返さないものである。   At that time, the hub 6 shape, the front shroud 2 shape, and the rear shroud 3 shape having a flow path shape in which the flow path cross-sectional area change from the inlet 5 to the outlet 25 including the inducer 8 of the impeller 1 is only in the expansion direction. As a result, the flow velocity of the component (component in the cross-sectional direction of the rotating shaft 16) caused by the flow rate inside the impeller 1 is gradually and gradually reduced over the entire flow path region from the inlet 5 to the outlet 25 (FIG. 4). (B)), acceleration and rapid deceleration are not repeated.

以上のように、本実施の形態においては、インペラ１のインデューサ８を含めた入口５から出口２５までの流路断面積変化を拡大させた構成とすることにより、インペラ１内部の流量に起因する成分（回転軸１６断面方向の成分）の流速が入口５から出口２５までの全流路領域に渡って徐々に減速していき、加速や急減速を繰り返さないため、十分な送風効率の向上が図れるものである。   As described above, in the present embodiment, the change in the cross-sectional area of the flow path from the inlet 5 to the outlet 25 including the inducer 8 of the impeller 1 is increased, resulting in the flow rate inside the impeller 1. The flow rate of the component (the component in the cross-sectional direction of the rotating shaft 16) gradually decelerates over the entire flow path region from the inlet 5 to the outlet 25, and acceleration and sudden deceleration are not repeated. Can be achieved.

また、流路断面積変化は、図４（ｂ）に示すように、略直線状であることにより、インペラ１内部の流量に起因する成分（回転軸１６断面方向の成分）の流速が、回転軸１６断面の流れ方向に対して一定の割合で減速していくことで、急減速を発生させないものである。   Further, as shown in FIG. 4B, the flow path cross-sectional area change is substantially linear, so that the flow rate of the component due to the flow rate inside the impeller 1 (the component in the cross-sectional direction of the rotating shaft 16) is rotated. By decelerating at a constant rate with respect to the flow direction of the cross section of the shaft 16, sudden deceleration is not generated.

（実施の形態２）
次に、図５、図６に基づき、本発明の実施の形態２について説明する。電動送風機の基本構成は実施の形態１と同様であるのでその説明を省略する。 (Embodiment 2)
Next, a second embodiment of the present invention will be described with reference to FIGS. Since the basic configuration of the electric blower is the same as that of Embodiment 1, the description thereof is omitted.

本実施の形態では、図５（ａ）に示すように、インペラ１の流路断面積変化は、インペラの入口５からハブ終端部２６と、ハブ終端部２６から出口２５とで異なるものである。これにより、図５（ｂ）に示すように、インペラ１の流路中心曲線２１に並行な入口５から出口２５にかけての流速が変化するものである。   In the present embodiment, as shown in FIG. 5A, the change in the cross-sectional area of the flow path of the impeller 1 is different from the inlet 5 of the impeller to the hub terminal 26 and from the hub terminal 26 to the outlet 25. . Thereby, as shown in FIG. 5B, the flow velocity from the inlet 5 to the outlet 25 parallel to the flow path center curve 21 of the impeller 1 changes.

以上より、本実施の形態では、入口５からハブ終端部２６までと、ハブ終端部２６から出口２５までを分離して設計することができ、入口５側では吸引された流れが回転軸１６方向から径方向へ変る際に生じる剥離や渦、２次流れなどによる損失を低減する流路断面積変化を構成し、また出口２５側では径方向に排出するまでに生じる剥離や渦、円板回転摩擦損失などによる損失を低減する流路断面積変化を構成し、送風効率の向上が図れるものである。   As described above, in the present embodiment, it is possible to design the inlet 5 to the hub end portion 26 and the hub end portion 26 to the outlet 25 separately, and the suctioned flow is in the direction of the rotation axis 16 on the inlet 5 side. Detachment or vortex generated when changing from the radial direction to the radial direction, and a cross-sectional area change that reduces loss due to secondary flow, etc. The flow passage cross-sectional area change that reduces the loss due to friction loss and the like is configured, and the air blowing efficiency can be improved.

また、本実施の形態では、インペラ１の入口５からハブ終端部２６までの流路断面積変化が、ハブ終端２６部から出口２５までの流路断面積変化に比べて変化率が大きい構成としている。   In the present embodiment, the change in the flow passage cross-sectional area from the inlet 5 of the impeller 1 to the hub end 26 is larger than the change in the flow cross-sectional area from the hub end 26 to the outlet 25. Yes.

これにより、吸引された流れが回転軸１６方向から径方向へ変る際に生じる剥離や渦、２次流れで実際に空気が流れる面積が狭くなる場合に、流路断面積変化を略直線状に近付けることができ、インペラ１内部の流量に起因する成分（回転軸１６断面方向の成分）の流速が、回転軸１６断面の流れ方向に対して一定の割合で減速していくことで急減速を発生させないものである。   As a result, separation or vortex generated when the sucked flow changes from the direction of the rotary shaft 16 to the radial direction, and when the area where the air actually flows in the secondary flow becomes narrow, the change in the cross-sectional area of the flow path becomes substantially linear. The flow velocity of the component (component in the cross-sectional direction of the rotating shaft 16) caused by the flow rate inside the impeller 1 is decelerated at a constant rate with respect to the flow direction of the cross-section of the rotating shaft 16, and sudden deceleration is performed. It is not generated.

また、本実施の形態では、図６（ａ）（ｂ）に示すように、インペラ１の流路断面積変化は、インペラ１の入口５からハブ終端部２６と、ハブ終端部２６から出口２５とで異なり、かつそれぞれが略直線状であり、さらにハブ終端部２６近傍には入口５側と出口２５側の略直線状である流路断面積変化を接続する曲線変化部２７を有するものである。   Further, in the present embodiment, as shown in FIGS. 6A and 6B, the flow passage cross-sectional area of the impeller 1 changes from the inlet 5 of the impeller 1 to the hub terminal 26 and from the hub terminal 26 to the outlet 25. And each has a substantially linear shape, and further has a curve changing portion 27 in the vicinity of the hub terminal portion 26 for connecting a flow passage cross-sectional change that is substantially linear on the inlet 5 side and the outlet 25 side. is there.

これにより、インペラ１の入口５部からハブ終端部２６、そしてハブ終端部２６から出口２５へと円滑に流路断面積を変化させ、つまり流量に起因する成分（回転軸１６断面方向の成分）の流速を滑らかに減速させることができる。   As a result, the flow path cross-sectional area is smoothly changed from the inlet 5 portion of the impeller 1 to the hub terminal portion 26 and from the hub terminal portion 26 to the outlet 25, that is, a component caused by the flow rate (component in the cross-sectional direction of the rotating shaft 16). Can be smoothly decelerated.

（実施の形態３）
次に、図７に基づき、本発明の実施の形態３について説明する。電動送風機の基本構成は実施の形態１と同様であるのでその説明を省略する。 (Embodiment 3)
Next, Embodiment 3 of the present invention will be described with reference to FIG. Since the basic configuration of the electric blower is the same as that of Embodiment 1, the description thereof is omitted.

本実施の形態では、図７（ａ）（ｂ）に示すように、インペラ１は、前面シュラウド２およびハブ６の入口５端部近傍に回転軸１６方向と略平行な平行部２８を有し、回転軸１６に平行な円環状の吸気通路を構成している。   In the present embodiment, as shown in FIGS. 7A and 7B, the impeller 1 has a parallel portion 28 substantially parallel to the direction of the rotation axis 16 in the vicinity of the front shroud 2 and the inlet 5 end of the hub 6. An annular intake passage parallel to the rotating shaft 16 is formed.

これにより、インペラ１入口で回転軸１６方向に吸引させることで吸引時の乱れを低減し、その後、全ての回転軸１６方向の流れを径方向の流れに円滑に変化させることができる。   Thereby, the disturbance at the time of attraction | suction can be reduced by making it suck | suck to the rotating shaft 16 direction by the impeller 1 entrance, and the flow of all the rotating shafts 16 direction can be smoothly changed into the flow of radial direction after that.

（実施の形態４）
次に、図８に基づき、本発明の実施の形態３について説明する。電動送風機の基本構成は実施の形態１と同様であるのでその説明を省略する。 (Embodiment 4)
Next, Embodiment 3 of the present invention will be described with reference to FIG. Since the basic configuration of the electric blower is the same as that of Embodiment 1, the description thereof is omitted.

本実施の形態では、インペラ１を構成するインデューサ８を樹脂製とし、前面シュラウド２、後面シュラウド３およびブレード４を板金製としたものである。そして、ハブ終端部２６において流路断面積を回転軸１６方向と平行な断面から得る構成としている。つまり、後面シュラウド３が回転軸１６と垂直な関係にある場合、ハブ終端部２６での流路断面定義直線２２（入口案内翼７側、ブレード４側の両者）は後面シュラウド３に対して垂直な構成としている。   In the present embodiment, the inducer 8 constituting the impeller 1 is made of resin, and the front shroud 2, the rear shroud 3, and the blade 4 are made of sheet metal. In the hub terminal portion 26, the flow path cross-sectional area is obtained from a cross section parallel to the direction of the rotation axis 16. That is, when the rear surface shroud 3 is perpendicular to the rotating shaft 16, the flow path cross-sectional definition straight line 22 (both on the inlet guide vane 7 side and the blade 4 side) at the hub end portion 26 is perpendicular to the rear surface shroud 3. It has a simple structure.

これにより、材質および製造方法の異なるインペラ１の入口５側であるインデューサ８部の流路と、出口２５側である板金部の流路（前面シュラウド２と後面シュラウド３で挟まれた流路）を個別に製作することができ、簡易にインペラ１を構成することができる。   Thereby, the flow path of the inducer 8 part on the inlet 5 side of the impeller 1 of different material and manufacturing method and the flow path of the sheet metal part on the outlet 25 side (the flow path sandwiched between the front shroud 2 and the rear shroud 3) ) Can be manufactured individually, and the impeller 1 can be configured easily.

なお、上記した各実施の形態１〜４においては、入口案内翼７とブレード４の翼厚さ（板厚）を考慮し、実際に気流がスムーズに通過するように流路を構成することが望ましい。   In each of the above-described first to fourth embodiments, the flow path may be configured so that the airflow actually passes smoothly in consideration of the blade thickness (plate thickness) of the inlet guide blade 7 and the blade 4. desirable.

（実施の形態５）
図９は、本発明の実施の形態５における電気掃除機を示している。 (Embodiment 5)
FIG. 9 shows a vacuum cleaner according to Embodiment 5 of the present invention.

図に示すように、掃除機本体２９内に電動送風機３０を有し、吸引ノズル３１から空気流とともに塵埃を吸引し、集塵室３２に塵埃を蓄える。   As shown in the figure, an electric blower 30 is provided in the cleaner body 29, and dust is sucked together with the air flow from the suction nozzle 31, and dust is stored in the dust collecting chamber 32.

ここで、電動送風機３０として各実施の形態１〜４で示したいずれかの電動送風機を用いることにより、吸引性能を高めることができ、さらには消費エネルギーを抑えた電気掃除機を実現することができる。   Here, by using any one of the electric blowers shown in the first to fourth embodiments as the electric blower 30, it is possible to improve the suction performance and further to realize a vacuum cleaner with reduced energy consumption. it can.

以上のように、本発明にかかる電動送風機は、十分な送風効率の向上が図れるものであるので、電気掃除機としてはもちろんのこと、他の家庭用電化機器、産業機器などの用途にも幅広く適用できる。さらには、電動送風機は同様の観点において、圧縮機、タービン、液体用ポンプにも適用可能である。   As described above, since the electric blower according to the present invention can sufficiently improve the blowing efficiency, it can be widely used not only as a vacuum cleaner but also for other household appliances and industrial equipment. Applicable. Furthermore, the electric blower can be applied to a compressor, a turbine, and a liquid pump from the same viewpoint.

本発明の実施の形態１における電動送風機の半断面図Half sectional view of electric blower in Embodiment 1 of the present invention 同電動送風機のインペラを一部切欠して示す平面図Top view showing the impeller of the electric blower with a part cut away 同電動送風機のインペラの断面図Cross section of the impeller of the electric blower （ａ）同電動送風機のインペラの流路中心曲線上における入口からの距離と流路中心曲線に垂直な流路断面積の関係を示すグラフ（ｂ）同インペラの流路中心曲線上の入口からの距離と流路中心曲線に並行な流速の関係を示すグラフ(A) Graph showing the relationship between the distance from the inlet on the channel center curve of the impeller of the electric blower and the channel cross-sectional area perpendicular to the channel center curve (b) From the inlet on the channel center curve of the impeller Graph showing the relationship between the distance of the flow and the flow velocity parallel to the flow path center curve （ａ）本発明の実施の形態２における電動送風機のインペラの流路中心曲線上における入口からの距離と流路中心曲線に垂直な流路断面積の関係を示すグラフ（ｂ）同インペラの流路中心曲線上の入口からの距離と流路中心曲線に並行な流速の関係を示すグラフ(A) Graph showing the relationship between the distance from the inlet on the flow path center curve of the impeller of the electric blower according to Embodiment 2 of the present invention and the flow path cross-sectional area perpendicular to the flow path center curve (b) Flow of the impeller Graph showing the relationship between the distance from the entrance on the path center curve and the flow velocity parallel to the path center curve （ａ）同他のインペラの流路中心曲線上における入口からの距離と流路中心曲線に垂直な流路断面積の関係を示すグラフ（ｂ）同インペラの流路中心曲線上の入口からの距離と流路中心曲線に並行な流速の関係を示すグラフ(A) Graph showing the relationship between the distance from the inlet on the flow path center curve of the other impeller and the cross-sectional area of the flow path perpendicular to the flow path center curve (b) From the inlet on the flow path center curve of the impeller Graph showing the relationship between distance and flow velocity parallel to the flow path center curve （ａ）本発明の実施の形態３における電動送風機のインペラの断面図（ｂ）同インペラの流路中心曲線上の入口からの距離と流路中心曲線に垂直な流路断面積の関係を示すグラフ(A) Cross section of impeller of electric blower in Embodiment 3 of the present invention (b) The relationship between the distance from the inlet on the flow path center curve of the impeller and the flow path cross-sectional area perpendicular to the flow path center curve is shown. Graph （ａ）本発明の実施の形態４における電動送風機のインペラ形状を示す分解断面図（ｂ）同インペラの流路中心曲線上の入口からの距離と流路中心曲線に垂直な流路断面積の関係を示すグラフ(A) Exploded sectional view showing the impeller shape of the electric blower in Embodiment 4 of the present invention (b) The distance from the inlet on the flow path center curve of the impeller and the flow path cross-sectional area perpendicular to the flow path center curve Graph showing relationship 本発明の実施の形態５における電気掃除機の断面図Sectional drawing of the vacuum cleaner in Embodiment 5 of this invention 従来の電動送風機におけるインペラの断面図Cross section of impeller in conventional electric blower （ａ）同インペラ直径と流路円筒断面積の関係を示すグラフ（ｂ）同インペラ直径と径方向流速の関係を示すグラフ(A) Graph showing the relationship between the impeller diameter and the flow path cylindrical cross-sectional area (b) Graph showing the relationship between the impeller diameter and the radial flow velocity

符号の説明Explanation of symbols

１ インペラ
２ 前面シュラウド
３ 後面シュラウド
４ ブレード
５ 入口
６ ハブ
７ 入口案内翼
８ インデューサ
９ 静翼
１０ 基板
１１ エアガイド
１２ 吸気孔
１３ ケーシング
１４ 電動機
１６ 回転軸
２５ 出口
２６ ハブ終端部
２７ 曲線変化部
２８ 平行部
３０ 電動送風機 DESCRIPTION OF SYMBOLS 1 Impeller 2 Front shroud 3 Rear shroud 4 Blade 5 Inlet 6 Hub 7 Inlet guide vane 8 Inducer 9 Stator vane 10 Substrate 11 Air guide 12 Intake hole 13 Casing 14 Electric motor 16 Rotating shaft 25 Outlet 26 Hub end part 27 Curve changing part 28 Parallel part 30 Electric blower

Claims (8)

前面シュラウド、後面シュラウドおよび両シュラウド間の複数枚のブレードとを有するインペラと、前記インペラの入口内部に配した山型のハブおよび入口案内翼とを有するインデューサと、前記インペラの外周に位置した複数枚の静翼およびその基板とを有するエアガイドと、前記エアガイドとともにインペラを内包し中央に吸気孔を有したケーシングと、前記インペラを回転駆動させる電動機とを備え、前記インペラのインデューサを含めた入口から出口までの流路断面積変化を拡大させた電動送風機。 An impeller having a front shroud, a rear shroud, and a plurality of blades between the shrouds, an angler hub and an inlet guide vane disposed inside the inlet of the impeller, and an outer periphery of the impeller An air guide having a plurality of stationary blades and a substrate thereof, a casing including an impeller together with the air guide and having a suction hole in the center thereof, and an electric motor that rotationally drives the impeller, an inducer of the impeller Electric blower with expanded cross-sectional area change from the included inlet to outlet. 流路断面積変化は、略直線状である請求項１に記載の電動送風機。 The electric blower according to claim 1, wherein the flow path cross-sectional area change is substantially linear. 流路断面積変化は、インペラの入口からハブ終端部と、ハブ終端部から出口とで異なる請求項１または２に記載の電動送風機。 3. The electric blower according to claim 1, wherein the change in the cross-sectional area of the flow path is different from the inlet end of the impeller to the hub end portion and from the hub end portion to the outlet. インペラの入口からハブ終端部までの流路断面積変化が、ハブ終端部から出口までの流路断面積変化に比べて変化率が大きい構成とした請求項３に記載の電動送風機。 The electric blower according to claim 3, wherein the change rate of the flow passage cross-sectional area from the inlet of the impeller to the end of the hub is larger than the change of flow cross-sectional area from the end of the hub to the outlet. 流路断面積変化は、インペラの入口からハブ終端部と、ハブ終端部から出口とで異なり、かつそれぞれが略直線状であり、さらにハブ終端部近傍には入口側と出口側の流路断面積変化を接続する曲線変化部を有する請求項１に記載の電動送風機。 The change in the cross-sectional area of the flow path differs from the impeller inlet to the hub end and from the hub end to the outlet, and is substantially linear. The electric blower according to claim 1, further comprising a curve changing portion connecting the area changes. インペラは、前面シュラウドおよびハブの入口部に回転軸方向と平行な平行部を有する請求項１〜５のいずれか１項に記載の電動送風機。 6. The electric blower according to claim 1, wherein the impeller has a parallel portion parallel to the rotation axis direction at an entrance portion of the front shroud and the hub. インデューサを樹脂製とし、前面シュラウド、後面シュラウドおよびブレードを板金製とした請求項１〜６のいずれか１項に記載の電動送風機。 The electric blower according to any one of claims 1 to 6, wherein the inducer is made of resin, and the front shroud, the rear shroud, and the blade are made of sheet metal. 請求項１〜７のいずれか１項に記載の電動送風機を有する電気掃除機。 The vacuum cleaner which has an electric blower of any one of Claims 1-7.
JP2006307424A 2006-11-14 2006-11-14 Electric blower and electric vacuum cleaner using the same Active JP4867596B2 (en)

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CNU2007201396980U CN201037473Y (en) 2006-11-14 2007-04-12 Electric motor and electric dust collector using the same
CNB2007100967749A CN100516546C (en) 2006-11-14 2007-04-12 Electric blower and electric cleaner using the same
EP07012832.7A EP1923572B1 (en) 2006-11-14 2007-06-29 Electric blower and electric cleaner using the same
KR1020070066813A KR101287250B1 (en) 2006-11-14 2007-07-04 Electric blower and electric cleaner using the same

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EP1923572A3 (en) 2010-10-20
CN100516546C (en) 2009-07-22
CN101182851A (en) 2008-05-21
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CN201037473Y (en) 2008-03-19
KR20080043684A (en) 2008-05-19

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