JP2016125437A - Electric blower and vacuum cleaner - Google Patents
Electric blower and vacuum cleaner Download PDFInfo
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- JP2016125437A JP2016125437A JP2015001232A JP2015001232A JP2016125437A JP 2016125437 A JP2016125437 A JP 2016125437A JP 2015001232 A JP2015001232 A JP 2015001232A JP 2015001232 A JP2015001232 A JP 2015001232A JP 2016125437 A JP2016125437 A JP 2016125437A
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Abstract
Description
本発明は、電動送風機及びそれを搭載した電気掃除機に関する。 The present invention relates to an electric blower and a vacuum cleaner equipped with the electric blower.
本技術分野の背景技術として、例えば、特開平４−３３０３９８号公報（特許文献１）がある。回転軸に一体固定される遠心羽根車及び中央を前記回転軸が、貫通し、該遠心羽根車の後段に位置する固定案内羽根を有する、多段式の送風機において、前記固定案内羽根内周面に環状の凸部を設け、該凸部と前記回転軸の外周との間に微少隙間を有したことを特徴とする送風機、と記載されている。 As background art of this technical field, for example, there is JP-A-4-330398 (Patent Document 1). In a multistage blower having a centrifugal impeller that is integrally fixed to a rotary shaft and a fixed guide vane that passes through the center of the centrifugal impeller and is located at the rear stage of the centrifugal impeller, on the inner peripheral surface of the fixed guide blade An air blower characterized in that an annular convex portion is provided and a minute gap is provided between the convex portion and the outer periphery of the rotating shaft.
従来の発明の特許文献１は、多段式の遠心羽根車が示されており、初段の羽根車と後段の羽根車との間の回転軸周りに生じる漏れ流れの抑制構造とその効果について記載されている。また、電気掃除機の電動送風機に対して、特許文献１の発明である送風機を適用して、効率向上を図った例が示されている。従来技術で示されている電動送風機の構造は，効率が向上するため、吸込仕事率を高めることが可能である。 Patent Document 1 of the conventional invention shows a multistage centrifugal impeller, and describes a structure for suppressing a leakage flow around a rotation axis between an initial stage impeller and a rear stage impeller and its effect. ing. Moreover, the example which applied the air blower which is invention of patent document 1 with respect to the electric air blower of a vacuum cleaner, and aimed at the efficiency improvement is shown. Since the efficiency of the electric blower structure shown in the prior art is improved, the suction power can be increased.
電気掃除機の吸込仕事率の測定方法は、JIS C ９１０８（２００９）「電気掃除機」で定められている。吸込仕事率は、風量と真空度の積から求まる空気力学的動力の測定値からなる空気力学的動力曲線の最大値のことである。高い吸込仕事率を実現するには、従来技術の電動送風機のように送風機の効率を向上する他に、電気掃除機の消費電力（電動送風機の消費電力）を大きくする方法がある。吸込仕事率の向上のために電動送風機の消費電力を増加する場合は、図３に示すように吸込仕事率を得る風量点（以下、吸込仕事率点）の電流を高めることが有効である。しかし、吸込仕事率点の電流を増加させると、吸込仕事率の向上は望めるが、掃除機の運転条件における最大電流が増加する。このため、一般的な家庭で用いられている電源コンセントの電流容量（１５Ａ）を超えるといった懸念がある。 The method for measuring the suction power of the vacuum cleaner is defined by JIS C 9108 (2009) “Electric vacuum cleaner”. The suction power is the maximum value of the aerodynamic power curve composed of measured values of aerodynamic power obtained from the product of the air volume and the degree of vacuum. In order to realize a high suction work rate, there is a method of increasing the power consumption of the vacuum cleaner (power consumption of the electric blower) in addition to improving the efficiency of the blower like the electric blower of the prior art. In order to increase the power consumption of the electric blower in order to improve the suction power, it is effective to increase the current at the air volume point (hereinafter referred to as the suction power point) for obtaining the suction power as shown in FIG. However, if the current at the suction power point is increased, an improvement in the suction power can be expected, but the maximum current in the operating condition of the cleaner increases. For this reason, there is a concern that the current capacity (15 A) of a power outlet used in a general home is exceeded.
また、吸込仕事率点の電流を増加させるには、電動機の高トルク化、送風機の軸動力の増加、もしくは両者が必要となる。電流を高めた場合，電動機の電流増加と、送風機の軸動力の増加により電動送風機の効率が低下する。すなわち、吸込仕事率点の電流を増加させた場合は，電動送風機の効率低下を防ぐ必要がある。 In order to increase the current at the suction power point, it is necessary to increase the torque of the electric motor, increase the axial power of the blower, or both. When the current is increased, the efficiency of the electric blower decreases due to an increase in the electric current of the electric motor and an increase in the shaft power of the blower. In other words, when the current at the suction power point is increased, it is necessary to prevent a reduction in the efficiency of the electric blower.
そこで本発明は、吸込仕事率の向上と、最大電流を家庭用電源コンセントの上限値（１５Ａ未満）以下に低減することを両立した電動送風機及びそれを搭載した電気掃除機を提供することを目的としている。 Then, this invention aims at providing the electric blower which improved the suction work rate, and reduced the maximum electric current below the upper limit (less than 15A) of a household power outlet, and a vacuum cleaner carrying the same. It is said.
また、本発明は、吸込仕事率点の電流を増加させた場合に、最大電流を家庭用電源コンセントの上限値（１５Ａ未満）以下に低減し、送風機の効率も高めることで吸込仕事率の向上が可能な電動送風機及びそれを搭載した電気掃除機を提供することを目的としている。 In addition, when the current at the suction power point is increased, the present invention improves the suction power by reducing the maximum current below the upper limit (less than 15A) of the household power outlet and increasing the efficiency of the blower. It aims at providing the electric blower which can be used, and the vacuum cleaner carrying the same.
上記の目的を達成するため、例えば、特許請求の範囲に記載の構成を採用する。 In order to achieve the above object, for example, the configuration described in the claims is adopted.
本発明は上記課題を解決する手段を多数含んでいるが、その一例を挙げるならば、本発明は、ハブと、円周方向に複数配置される羽根からなる羽根車と、前記羽根車を回転させる電動機とを備え，前記羽根車を電動機の軸方向に複数段形成した電動送風機において、最終段の羽根車上流のリターンガイドの子午面形状を形成するシュラウド面，ハブ面がともに、半径方向の内側へ向かうにつれ回転軸の軸方向上流側へ緩やかに傾斜した構成にすることを特徴とする。 The present invention includes a number of means for solving the above problems. For example, the present invention relates to a hub, an impeller composed of a plurality of blades arranged in the circumferential direction, and the impeller. In the electric blower in which the impeller is formed in a plurality of stages in the axial direction of the motor, both the shroud surface and the hub surface that form the meridional shape of the return guide upstream of the final stage impeller are arranged in the radial direction. As it goes inward, the structure is characterized in that it is gently inclined toward the upstream side in the axial direction of the rotating shaft.
本発明によれば、吸込仕事率の向上と、最大電流を家庭用電源コンセントの上限値（１５Ａ未満）以下に低減することを両立した電動送風機及びそれを搭載した電気掃除機を提供することが可能となる。 According to the present invention, it is possible to provide an electric blower that achieves both improvement in suction work rate and reduction of the maximum current below the upper limit (less than 15A) of a household power outlet, and a vacuum cleaner equipped with the electric blower. It becomes possible.
また、本発明によれば、吸込仕事率点の電流を増加させた場合に、最大電流を電源コンセントの上限値（１５Ａ未満）以下に低減し、送風機の効率も高めることで吸込仕事率を向上した電動送風機及びそれを搭載した電気掃除機を提供することが可能となる。
In addition, according to the present invention, when the current at the suction power point is increased, the maximum current is reduced to the upper limit value (less than 15A) of the power outlet, and the efficiency of the blower is improved, thereby improving the suction power. It becomes possible to provide an electric blower and a vacuum cleaner equipped with the electric blower.
以下、本発明の実施例１から実施例３を図に基づいて詳説する。 Embodiments 1 to 3 of the present invention will be described below in detail with reference to the drawings.
以下、本発明の一実施例を、図面を用いて説明する。 Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
まず、図１を用いて、電気掃除機全体について説明する。図１に模式的に示した電気掃除機本体１００の上から見た横断面図において、電気掃除機本体１００の構成を説明する。電気掃除機本体１００に着脱自在なホース継ぎ手１０１を装着する側を電気掃除機本体１００の前側とする。 First, the whole vacuum cleaner will be described with reference to FIG. The configuration of the vacuum cleaner main body 100 will be described with reference to a cross-sectional view seen from above of the vacuum cleaner main body 100 schematically shown in FIG. The side where the hose joint 101 detachably attached to the vacuum cleaner main body 100 is set as the front side of the vacuum cleaner main body 100.
電気掃除機本体１００の前側に、紙パック１０３を保持するための集塵室１０２を備え、電気掃除機本体１００の後側に、電動送風機１０６を収納するためのモータ室１０５を備え、集塵室１０２とモータ室１０５との間に、万一、紙パック１０３から塵埃が漏れ出ても、集塵室１０２内の塵埃がモータ室１０５へ流入するのを抑制するためのフィルタ部１０４を備える。集塵室１０２とモータ室１０５とは、フィルタ部１０４を介して連通する。集塵室１０２には、着脱自在な紙パック１０３を備える。紙パック１０３の開口がホース継ぎ手１０１に連通する。紙パック１０３内に塵埃が堆積していくと、紙パック１０３が膨らみ、紙パック１０３の開口と反対側の底部がフィルタ部１０４に当接するようになる。モータ室１０５に、吸引力を発生する電動送風機１０６を備える。電動送風機１０６の前端とモータ室１０５の前側の壁面との間に、電動送風機１０６の振動が電気掃除機本体１００に伝達することを抑制するための防振ゴム１０７（防振部材）を備える。防振部材は、ゴムの代わりバネであってもよい。電動送風機１０６は、前端に、空気を吸い込むための送風機入口１０８を備え、後側の側方に、空気を排出するための送風機出口１０９を備える。そして、送風機入口１０８がフィルタ部１０４に対して開口している。モータ室１０５の側方に、電源コードを巻きつけて収納するためのコードリール１１０を備える。また、電動送風機の電流を感知し、運転条件を制御する制御回路１１２を備える。また、電気掃除機本体１００の後側両側方に、車輪１１１を備える。なお、図示しないが、ホース継ぎ手１０１には、ホースが接続され、ホースには、操作管が接続され、操作管には、延長管が接続され、延長管には、吸込具が接続される。 A dust collection chamber 102 for holding the paper pack 103 is provided on the front side of the vacuum cleaner main body 100, and a motor chamber 105 for housing the electric blower 106 is provided on the rear side of the vacuum cleaner main body 100. A filter unit 104 is provided between the chamber 102 and the motor chamber 105 to prevent the dust in the dust collection chamber 102 from flowing into the motor chamber 105 even if dust leaks from the paper pack 103. . The dust collection chamber 102 and the motor chamber 105 communicate with each other via the filter unit 104. The dust collection chamber 102 includes a detachable paper pack 103. The opening of the paper pack 103 communicates with the hose joint 101. As dust accumulates in the paper pack 103, the paper pack 103 swells and the bottom of the paper pack 103 opposite to the opening comes into contact with the filter unit 104. The motor chamber 105 includes an electric blower 106 that generates a suction force. Between the front end of the electric blower 106 and the wall surface on the front side of the motor chamber 105, a vibration-proof rubber 107 (vibration-proof member) for suppressing the vibration of the electric blower 106 from being transmitted to the electric vacuum cleaner main body 100 is provided. The vibration isolation member may be a spring instead of rubber. The electric blower 106 includes a blower inlet 108 for sucking air at the front end, and a blower outlet 109 for discharging air on the side of the rear side. The blower inlet 108 is open to the filter unit 104. A cord reel 110 is provided on the side of the motor chamber 105 to wind and store a power cord. Moreover, the control circuit 112 which senses the electric current of an electric blower and controls an operation condition is provided. In addition, wheels 111 are provided on both sides of the rear side of the vacuum cleaner main body 100. Although not shown, a hose is connected to the hose joint 101, an operation pipe is connected to the hose, an extension pipe is connected to the operation pipe, and a suction tool is connected to the extension pipe.
次に、電気掃除機本体１００内の空気の流れを説明する。ホース継ぎ手１０１から流入した空気は、集塵室１０２に入る。図１は集塵手段として紙パック１０３が示されているが、パックの素材は問わない。また、サイクロン方式の場合は、サイクロン室（サイクロン式集塵ケース）が紙パック１０３の代わりに収まる。紙パック１０３で塵埃を取り除かれた空気は、その後モータ室１０５に流入する。電動送風機１０６は、モータ室１０５に防振ゴム１０７を介して設置されており、送風機入口１０８から流入した空気は昇圧された後、送風機出口１０９から排気され、図示してないが、電気掃除機本体１００の排気口から外部に排出される。 Next, the flow of air in the vacuum cleaner main body 100 will be described. Air flowing in from the hose joint 101 enters the dust collection chamber 102. Although FIG. 1 shows a paper pack 103 as the dust collecting means, the material of the pack is not limited. In the case of the cyclone method, a cyclone chamber (a cyclone dust collecting case) is accommodated instead of the paper pack 103. The air from which dust has been removed by the paper pack 103 then flows into the motor chamber 105. The electric blower 106 is installed in the motor chamber 105 via a vibration isolating rubber 107, and the air flowing from the blower inlet 108 is pressurized and then exhausted from the blower outlet 109. Although not shown, the electric vacuum cleaner It is discharged from the exhaust port of the main body 100 to the outside.
次に、図２を用いて、電動送風機１０６について説明する。なお、図２では電動送風機１０６を２００とし説明する。電動送風機２００は、空気を吸い込むための送風機２０１と送風機２０１を駆動するための電動機２０２から構成されている。なお、図２は回転軸２０５の軸方向が、電気掃除機本体１００の前後方向に略一致する。回転軸２０５を基準として、軸方向に直行する方向が半径方向である。 Next, the electric blower 106 will be described with reference to FIG. In FIG. 2, the electric blower 106 is described as 200. The electric blower 200 includes a blower 201 for sucking air and an electric motor 202 for driving the blower 201. In FIG. 2, the axial direction of the rotary shaft 205 substantially coincides with the front-rear direction of the electric vacuum cleaner main body 100. A direction orthogonal to the axial direction with respect to the rotation shaft 205 is a radial direction.
電動機２０２は、ハウジング２０３及びエンドブラケット２０４からなる電動機外殻に、軸受２１８を介して回転軸２０５が支持され、回転軸２０５にはロータ２０６が取り付けられる。ロータ２０６の外周には固定部のステータ２０７が配置される。回転部のロータ２０６への電気の供給は、ブラシ２０８とそれに接触するコンミテータ２０９により伝えられている。 In the electric motor 202, a rotating shaft 205 is supported on a motor outer shell including a housing 203 and an end bracket 204 via a bearing 218, and a rotor 206 is attached to the rotating shaft 205. A fixed portion stator 207 is arranged on the outer periphery of the rotor 206. The supply of electricity to the rotor 206 of the rotating part is transmitted by a brush 208 and a commutator 209 that contacts the brush 208.
図２は代表例として、送風機２０１にシュラウド２３０を有する２つの羽根車を持つ２段送風機を図示している。 FIG. 2 illustrates a two-stage blower having two impellers having a shroud 230 in the blower 201 as a representative example.
送風機２０１は、回転軸２０５に直結され，軸方向に複数個の羽根車２１０、２２０が設置されている。また、前記羽根車の外周側に設けられたディフューザ２１１、２２１と、ディフューザに対して仕切り板２１２、２２２を挟んで対面に配置されるリターンガイド２１３、２２３が、ファンケーシング２１４内に収められた構成である。 The blower 201 is directly connected to the rotary shaft 205, and a plurality of impellers 210 and 220 are installed in the axial direction. Further, diffusers 211 and 221 provided on the outer peripheral side of the impeller, and return guides 213 and 223 disposed on the opposite sides of the diffuser with the partition plates 212 and 222 interposed therebetween, were housed in the fan casing 214. It is a configuration.
最終段の羽根車２２１は、回転軸２０５に設けられた段差と，回転軸２０５と同軸のカラー２３１によって軸方向位置が固定されている。また、カラーの軸方向位置は、前記カラー２３１の軸方向上流に、前段の羽根車２１０が設置され、締付部材２３８で固定されている。回転軸２０５には各段の羽根車の周方向位置を決める構造（例えば、Ｄカット）が用いられている。なお、カラー２３１は、最終段の羽根車内部と軸方向に重なる部分において、羽根車のハブ面２２６に向かってカラー２３１の外径が緩やかに大きくなるように構成し、羽根車へ流入する流れの均一化を図っている。 The final stage impeller 221 has an axial position fixed by a step provided on the rotary shaft 205 and a collar 231 coaxial with the rotary shaft 205. Further, the position of the collar in the axial direction is such that the preceding stage impeller 210 is installed upstream of the collar 231 in the axial direction and is fixed by a fastening member 238. The rotating shaft 205 uses a structure (for example, D cut) that determines the circumferential position of each stage of the impeller. The collar 231 is configured such that the outer diameter of the collar 231 gradually increases toward the hub surface 226 of the impeller at a portion overlapping the inside of the final stage impeller in the axial direction, and flows into the impeller. To equalize.
また、羽根車２１０、２２０は、目玉部２１５、２２９において、ファンケーシング２１４とマウスリング２２４に具備されたシール材２１６と概略接触しており、空気の漏れ、つまり循環流を防ぐ構造を有している。また、最終段を除く各段の羽根車の背面には、羽根車に設けられた突起２３５とシール材２３６が概略接触しており、各段の間の空気の漏れを防ぐ構造を有している。すなわち、本送風機は羽根車を構成する部位が、回転軸の軸方向に、シール材に概略接触する３つ以上のシール構造を有している。このため、多段送風機の場合の段間の漏れ流れの防止ができ、効率向上が可能である。 Further, the impellers 210 and 220 are substantially in contact with the sealing material 216 provided on the fan casing 214 and the mouth ring 224 at the eyeball portions 215 and 229, and have a structure for preventing air leakage, that is, circulation flow. ing. Further, the rear surface of the impeller of each stage except the final stage is substantially in contact with the projection 235 provided on the impeller and the sealing material 236, and has a structure that prevents air leakage between each stage. Yes. In other words, the blower has three or more seal structures in which the portion constituting the impeller substantially contacts the seal material in the axial direction of the rotation shaft. For this reason, the leakage flow between stages in the case of a multistage blower can be prevented, and the efficiency can be improved.
ディフューザ２１１の子午面形状（回転軸心を含む平面）は、シュラウド側のリング２１９と仕切り板２１２で構成されている。また、曲がり部２３２の子午面形状は、ファンケーシング２１４とマウスリング２２４から構成され，緩やかな形状で半径方向の外向きに向いた流れを内向きに略１８０゜転向させている。なお、曲がり部２３２の子午面形状は、リング２１９とマウスリング２２４から形成されていてもよい。リターンガイド２１３は仕切り板２１２と一体で構成されている。リターンガイド２１３の子午面形状は、ハブ面を形成する仕切り板２１２と、シュラウド面を形成するマウスリングがともに半径方向の内側に向かうにつれて、軸方向の上流側へ緩やかに傾斜している。また、マウスリング２２４は，羽根車入口に流れを案内する曲率部２２７を有している。なお、曲がり部からマウスリングの曲率部を含んだ子午面形状は、軸方向下流に向かった後、軸方向上流へと緩やかに傾斜し、その後、最終段の入口に向かうために軸方向下流に曲がった形状となっている。最終段の羽根車下流に設けたディフューザ２２０は、シュラウド側のリング２２５と、ディフューザ翼と仕切り板２２２から構成され、その下流には他の段と同様にリターンガイド２２３が設置されている。なお、前記マウスリング２２４は、最終段のディフューザのリング２２５と軸芯を出すために、嵌め合い部２２８を有している。また、前記マウスリング２２４は、最終段のディフューザのリング２２５とネジ等で固定され、部品間の合わせ面に樹脂製のシール材が設けられ、ディフューザ流路の漏れを防止している。 The meridian shape (a plane including the rotation axis) of the diffuser 211 is configured by a shroud side ring 219 and a partition plate 212. Further, the meridional shape of the bent portion 232 is composed of the fan casing 214 and the mouth ring 224, and the gentle outward shape turns the outwardly directed flow in the radial direction by approximately 180 °. The meridional shape of the bent portion 232 may be formed from the ring 219 and the mouth ring 224. The return guide 213 is configured integrally with the partition plate 212. The meridional shape of the return guide 213 is gently inclined toward the upstream side in the axial direction as the partition plate 212 forming the hub surface and the mouth ring forming the shroud surface both go radially inward. The mouth ring 224 has a curvature portion 227 for guiding the flow to the impeller entrance. In addition, the meridional shape including the curvature part of the mouth ring from the bent part is gently inclined to the upstream in the axial direction after going to the downstream in the axial direction, and then downstream in the axial direction to go to the entrance of the final stage. It has a bent shape. The diffuser 220 provided downstream of the final stage impeller includes a shroud-side ring 225, a diffuser blade, and a partition plate 222, and a return guide 223 is installed on the downstream side in the same manner as the other stages. The mouth ring 224 has a fitting portion 228 for aligning with the ring 225 of the final stage diffuser. Further, the mouth ring 224 is fixed to the ring 225 of the final stage diffuser with screws or the like, and a sealing material made of resin is provided on the mating surface between the components to prevent leakage of the diffuser flow path.
ここで、初段の静止流路の部品構成は（ディフューザ２１１、曲がり部２３２、リターンガイド２１３を含む）、ディフューザ２１１、仕切り板２１２、リターンガイド２１３が例えば、樹脂製の一体成型品で構成され、これらを挟み込むように軸方向の上流側にリング２１３、下流側にマウスリング２２４が溶着もしくは、接着されていている。なお、リング２１３は、ディフューザの翼と接しており，リングと翼の先端は溶着や接着もしくは塗装、もしくはやわらかいゴムをかえして押し付けて設置されてもよい。 Here, the component configuration of the first-stage stationary flow path (including the diffuser 211, the bent portion 232, and the return guide 213), the diffuser 211, the partition plate 212, and the return guide 213 are configured by, for example, an integrally molded product made of resin, A ring 213 is welded or bonded to the upstream side in the axial direction and a mouth ring 224 is welded to the downstream side so as to sandwich them. The ring 213 is in contact with the wing of the diffuser, and the ring and the tip of the wing may be installed by welding, bonding, painting, or pressing soft rubber instead.
また、各段の静止流路には図２に示した嵌め合い部（例えば、２２８）が構成され、樹脂製のシール材により段間の漏れの防止と組み立て性の向上を図っている。 In addition, the stationary flow path of each stage is formed with a fitting part (for example, 228) shown in FIG. 2, and a resin sealing material prevents leakage between stages and improves assemblability.
また、最終段の羽根車の目玉部２２９は、上流のリターンガイドの子午面形状のうち、最も軸方向に下流の面２３４と比べて、軸方向の上流側に配置した構成としており、電動送風機の小型化を実現している。
In addition, the center part 229 of the impeller at the final stage is configured to be arranged on the upstream side in the axial direction of the meridional shape of the upstream return guide, compared to the downstream surface 234 in the most axial direction. The miniaturization is realized.
次に、電動送風機内部の流れについて説明する。図１の送風機入口１０８に相当する電動送風機入口２１７を通過した空気は、目玉部２１５近傍を通過した後、羽根車２１０で昇圧される。その後、ディフューザ２１１を通過した流れは曲がり部２３２で緩やかに略１８０゜転向し、リターンガイド２１３へと流入する。リターンガイド２１３へと流入した流れは、リターンガイド２１３により流れの旋回成分が低減され、半径方向の内向きに案内される。この過程において流れは減速されて、その分、圧力が上昇する。更に，リターンガイド２１３を通過した流れは、マウスリングの曲率部２２７部を通過した後、羽根車２２０で再度、昇圧される。その後、ディフューザ２２１を通過した流れは曲がり部２３３で略１８０゜転向し、リターンガイド２２３へと流入する。その後、電動機２０２のハウジング２０３内に流入し、ロータ２０６、ステータ２０７、ブラシ２０８、コンミテータ２０９などを冷却してから電動機外部へ排気される。
Next, the flow inside the electric blower will be described. The air that has passed through the electric blower inlet 217 corresponding to the blower inlet 108 in FIG. 1 passes through the vicinity of the centerpiece 215 and is then pressurized by the impeller 210. Thereafter, the flow that has passed through the diffuser 211 is gradually turned by approximately 180 ° at the bent portion 232 and flows into the return guide 213. The flow that has flowed into the return guide 213 is guided inward in the radial direction with the swirl component of the flow reduced by the return guide 213. In this process, the flow is decelerated, and the pressure increases accordingly. Furthermore, the flow that has passed through the return guide 213 passes through the curvature portion 227 of the mouth ring, and then is again pressurized by the impeller 220. Thereafter, the flow that has passed through the diffuser 221 is turned by approximately 180 ° at the bent portion 233 and flows into the return guide 223. Thereafter, it flows into the housing 203 of the electric motor 202, cools the rotor 206, the stator 207, the brush 208, the commutator 209, and the like and then exhausts the electric motor to the outside.
次に、本発明が対象とする電気掃除機の代表諸元について説明する。本発明に用いられる電動送風機の羽根車外径はおおよそφ４０mm〜φ１２０mmの範囲にあり、羽根出口高さはおおよそ５〜１２mmの範囲にあり、羽根の板厚はおおよそ０.５〜１.５mmの範囲にあり、羽根枚数はおおよそ６〜１３枚の範囲にあり、最高回転数はおおよそ毎分３０、０００〜１００、０００回転の範囲にある。また、電気掃除機の定格消費電力はおおよそ１０００Ｗを超え１５００Ｗ以下の範囲にある。 Next, representative specifications of the vacuum cleaner targeted by the present invention will be described. The impeller outer diameter of the electric blower used in the present invention is approximately in the range of φ40 mm to φ120 mm, the blade outlet height is in the range of approximately 5 to 12 mm, and the blade thickness is approximately in the range of 0.5 to 1.5 mm. The number of blades is in the range of approximately 6 to 13 and the maximum rotational speed is in the range of approximately 30,000 to 100,000 revolutions per minute. Moreover, the rated power consumption of the vacuum cleaner is in the range of more than about 1000 W and less than 1500 W.
なお、本実施の形態例ではシュラウドを有する羽根車を説明したが、シュラウドを有していないオープンタイプの羽根車でもよい。
In the present embodiment, an impeller having a shroud has been described. However, an open type impeller having no shroud may be used.
次に、図４を用いて、最終段（図では、２段目）の羽根車４０１の入口部に注目し，吸込仕事率点と最大電流となる風量時の流れの比較を示す。図４は図２で示した送風機部の一部と風の流れを示し、実線は吸込仕事率点を、点線は最大風量となる風量時の流れを示す。 Next, with reference to FIG. 4, focusing on the inlet portion of the impeller 401 at the final stage (second stage in the figure), a comparison is made between the suction power point and the flow at the time of the air flow at the maximum current. FIG. 4 shows a part of the blower unit shown in FIG. 2 and the flow of the wind, the solid line indicates the suction work point, and the dotted line indicates the flow at the time of the air volume that becomes the maximum air volume.
吸込仕事率点の流れ４０７は、前段の羽根車で昇圧された流れがディフューザを通り、曲がり部で略１８０゜転向され、リターンガイドに流入する。また、リターンガイドへ流入した流れは、リターンガイドの子午面形状を形成するシュラウド４０３、ハブ４０２が半径方向の内向きへ向かうにつれ軸方向の上流側へ緩やかに傾斜しているため，子午面形状に沿うように流れる。なお、リターンガイド出口の流れはリターンガイド内で旋回成分が低減され、マウスリングの曲率部４０４とカラー４０５の形状により、増速され最終段の羽根車４０１内へ流入される。マウスリングの曲率部の流れは、リターンガイドの子午面形状が軸方向の上流側に緩やかに傾斜しているため、羽根車入口での流れの転向が大きく，動作風量（速度）の影響を受けやすい。本実施例の最終段のマウスリング曲率部４０４の曲率半径は、約４ｍｍ〜８ｍｍ程度で構成している。
In the flow 407 at the suction work rate point, the flow boosted by the preceding impeller passes through the diffuser, is turned by approximately 180 ° at the bent portion, and flows into the return guide. In addition, the flow that flows into the return guide has a meridian shape because the shroud 403 and the hub 402 that form the meridional shape of the return guide are gently inclined toward the upstream side in the axial direction as the hub 402 goes inward in the radial direction. It flows along. The flow at the exit of the return guide is reduced in the swirl component in the return guide, and is accelerated by the shape of the curvature portion 404 and the collar 405 of the mouth ring and flows into the final stage impeller 401. The flow of the curvature part of the mouth ring is influenced by the operating air volume (speed) because the meridional shape of the return guide is gently inclined toward the upstream in the axial direction, and the flow direction at the impeller inlet is large. Cheap. The radius of curvature of the last stage mouth ring curvature portion 404 of this embodiment is about 4 mm to 8 mm.
吸込仕事率点のマウスリング曲率部の流れは、マウスリングの曲率に沿い剥離がなく最終段の羽根車４０１内に流入する。そのため、最終段の軸動力は他の段の羽根車と同等となる。また、送風機の高入力化を図る場合は、多段送風機であるために、１段あたりの軸動力を小さくできることから、羽根車内の風速を低減でき、摩擦損失の低減による高効率化と，低騒音化の両立が可能となる。さらに、リターンガイドの子午面形状が軸方向の上流側に緩やかに傾斜しているため、吸込仕事率点における最終段の羽根車入口流れを均一化でき、効率向上が図れる。 The flow of the mouth ring curvature portion at the suction work point flows into the impeller 401 at the final stage without peeling along the curvature of the mouth ring. Therefore, the final stage shaft power is equivalent to that of the other stage impellers. In order to increase the input of the blower, since it is a multistage blower, the shaft power per stage can be reduced, so the wind speed in the impeller can be reduced, the efficiency is improved by reducing friction loss, and the noise is reduced. It becomes possible to achieve both. Furthermore, since the meridional shape of the return guide is gently inclined toward the upstream side in the axial direction, the flow of the impeller inlet at the final stage at the suction work point can be made uniform, and the efficiency can be improved.
一方、最大電流時の風量は吸込仕事率点の風量に比べて約１．５倍と大きい。マウスリングの曲率部において、最大電流となる風量時の流れ４０８は、羽根車内部に向かう増速流れであり、吸込仕事率点に比べて流れが速い。このため、マウスリングの曲率部の流れは、曲率部の形状に流れが沿うことが出来ず、羽根車の前縁４０６において、軸方向に速度差が生じる。すなわち、最終段における最大電流時の羽根車前縁４０６の流れは、前縁のシュラウド側４０９が遅く、ハブ側４１０が速くなり偏った流れとなり、羽根車内の速度が不均一となる。このため、最大電流となる風量時の最終段の羽根車は、他の段の羽根車に比べて軸動力が小さくなる。
On the other hand, the air volume at the maximum current is about 1.5 times larger than the air volume at the suction power point. In the curvature portion of the mouth ring, the flow 408 at the time of the air volume that is the maximum current is a speed increasing flow toward the inside of the impeller, and the flow is faster than the suction work point. For this reason, the flow of the curvature portion of the mouth ring cannot follow the shape of the curvature portion, and a speed difference occurs in the axial direction at the front edge 406 of the impeller. That is, the flow of the impeller leading edge 406 at the maximum current in the final stage is a slow flow on the shroud side 409 of the front edge and a high speed on the hub side 410, and the speed in the impeller becomes uneven. For this reason, the last stage impeller at the time of the air volume which becomes the maximum current has a smaller shaft power than the other stage impellers.
図５に電流値を向上させ消費電力を高めた場合の、従来技術と本発明の構成による電流や空気力学的動力の特性の比較を示す。図５(a)に示した従来技術は、本実施例で説明したように動作風量に応じて最終段の羽根車の流れを積極的に変化させる構成（例えば、リターンガイドの子午面形状が半径方向内向きに向かうにつれ軸方向の上流側に緩やかに傾斜している構成）を有していない。このため、消費電力を高めた場合、最大電流となる風量時の軸動力が大きくなる。すなわち、最大電流が１５Ａを超えてしまうため、吸込仕事率点の高入力化ができず、吸込仕事率の向上が図れない。 FIG. 5 shows a comparison of characteristics of current and aerodynamic power according to the configuration of the prior art and the present invention when the current value is improved and the power consumption is increased. The prior art shown in FIG. 5A has a configuration in which the flow of the impeller at the final stage is actively changed according to the operating air volume as described in this embodiment (for example, the meridian shape of the return guide has a radius It has no structure that is gently inclined toward the upstream side in the axial direction as it goes inward. For this reason, when power consumption is raised, the shaft power at the time of the air volume which becomes the maximum electric current becomes large. That is, since the maximum current exceeds 15 A, it is not possible to increase the suction power point, and the suction power cannot be improved.
一方、図５(b)に示した本発明は、動作風量に応じて最終段の羽根車の流れを積極的に変化させる構成を持っているため、最大電流となる風量時の軸動力が低下し、最大電流が低下する。すなわち、吸込仕事率点の電流と最大電流との差を小さくできる。このため、本発明は、吸込仕事率点の高入力と、最大電流の低減が両立でき、吸込仕事率の向上が図れる。
On the other hand, the present invention shown in FIG. 5 (b) has a configuration in which the flow of the impeller at the final stage is actively changed according to the operating air volume, so that the shaft power at the time of the air volume at which the maximum current is reduced is reduced. However, the maximum current decreases. That is, the difference between the current at the suction power point and the maximum current can be reduced. For this reason, the present invention can achieve both high input of the suction power point and reduction of the maximum current, and can improve the suction power.
また、異なる電気環境においても同様な効果がある。例えば、使用電圧１１０Vの掃除機の吸込仕事率を消費電力で向上させる場合、電源コードの電流上限値（１５Ａ未満）を満足するため、最大電流の低減が必要である。そのため、最大電流を増加させることなく、吸込仕事率点の電流を増加させ、吸込仕事率の向上を図るには、実施例１に示した構成にすればよい。
Also, the same effect can be obtained in different electrical environments. For example, when the suction power of a cleaner with a working voltage of 110 V is improved with power consumption, the maximum current must be reduced to satisfy the current upper limit (less than 15 A) of the power cord. Therefore, in order to increase the current at the suction power point and increase the suction power without increasing the maximum current, the configuration shown in the first embodiment may be used.
実施例１と基本的な構成は同じであるので同一要素については同一符号を付してその説明を省略する。次に、図６を用いて、羽根車６００の形状について説明する。ここでは、図２中の送風機２０１に注目して記載し、送風機を６００とし説明する。 Since the basic configuration is the same as that of the first embodiment, the same elements are denoted by the same reference numerals and the description thereof is omitted. Next, the shape of the impeller 600 will be described with reference to FIG. Here, the blower 201 in FIG. 2 will be noted and described, and the blower will be described as 600.
送風機６００は、図２の送風機部分と同じように、シュラウドを有する２つの羽根車６０１、６０２を持つ２段送風機を図示している。送風機の基本的な構成は実施例１と同じなので省略する。 The blower 600 illustrates a two-stage blower having two impellers 601 and 602 having shrouds, similar to the blower portion of FIG. Since the basic configuration of the blower is the same as that of the first embodiment, a description thereof will be omitted.
図６のディフューザ６０５の子午面形状（回転軸心を含む平面）は、シュラウド側のリング６０３と仕切り板６０６で構成されている。また、曲がり部６０７の子午面形状は、ファンケーシング６０４とマウスリング６１０から構成され，緩やかな形状で半径方向の外向きに向いた流れを内向きへ略１８０゜転向させる。なお、曲がり部６０７の子午面形状は、リング６０３とマウスリング６１０から形成されていてもよい。リターンガイド６０８は仕切り板と一体で構成されている。リターンガイドのハブ面を構成する仕切り板６０６は略直線形状である。また、リターンガイドのシュラウド面を形成するマウスリング６１０は、羽根車入口に流れを案内する曲率部６０９を有している。なお、最終段の羽根車６０２の上流に設けたマウスリングの曲率部６０９の曲率半径は、約４ｍｍ〜８ｍｍ程度で構成されており、初段マウスリング曲率部６１７の半径に比べて大きい。最終段の羽根車下流に設けたディフューザ６１２は、シュラウド側のリング６１１と、ディフューザ翼と仕切り板６１５から構成されている。また、ディフューザの下流には曲がり部６１３と、他の段と同様にリターンガイド６１４が設置されている。 The meridional surface shape (plane including the rotation axis) of the diffuser 605 in FIG. 6 includes a ring 603 on the shroud side and a partition plate 606. The meridional shape of the bent portion 607 is composed of the fan casing 604 and the mouth ring 610, and turns the flow outward in the radial direction in a gentle shape by approximately 180 ° inward. The meridional shape of the bent portion 607 may be formed from the ring 603 and the mouth ring 610. The return guide 608 is configured integrally with the partition plate. The partition plate 606 constituting the hub surface of the return guide has a substantially linear shape. The mouth ring 610 forming the shroud surface of the return guide has a curvature portion 609 that guides the flow to the impeller inlet. The curvature radius of the mouth ring curvature portion 609 provided upstream of the final stage impeller 602 is about 4 mm to 8 mm, which is larger than the radius of the first stage mouth ring curvature portion 617. The diffuser 612 provided downstream of the final stage impeller includes a shroud-side ring 611, a diffuser blade, and a partition plate 615. Further, a bent portion 613 and a return guide 614 are installed on the downstream side of the diffuser like the other stages.
なお、前記マウスリング６１０は、最終段のディフューザのリング６１１と軸芯を出すために、嵌め合い部６１６を有している。また、前記マウスリング６１０は、最終段のディフューザのリング６１１とネジ等で固定され、部品間の合わせ面に樹脂製のシール材が設けられ、ディフューザ流路の漏れを防止している。 The mouth ring 610 has a fitting portion 616 in order to align with the ring 611 of the final stage diffuser. Further, the mouth ring 610 is fixed to the final stage diffuser ring 611 with a screw or the like, and a resin sealing material is provided on the mating surface between the components to prevent leakage of the diffuser flow path.
初段の静止流路の部品構成は（ディフューザ６０５、曲がり部６０７、リターンガイド６０８を含む）は、ディフューザ６０５、仕切り板６０６、リターンガイド６０８が例えば、樹脂製の一体成型品で構成され、これらを挟み込むように軸方向の上流側にリング６０３、下流側にマウスリング６１０が溶着もしくは、接着されていている。なお、リング６０３は、ディフューザの翼と接しており，リングと翼の先端は溶着や接着もしくは塗装、もしくはやわらかいゴムをかえして押し付けて設置されてもよい。 The component structure of the first-stage static flow path (including the diffuser 605, the bent portion 607, and the return guide 608) is configured such that the diffuser 605, the partition plate 606, and the return guide 608 are formed of, for example, an integrally molded resin product. A ring 603 is welded or bonded to the upstream side in the axial direction and a mouth ring 610 is welded to the downstream side so as to be sandwiched. The ring 603 is in contact with the wing of the diffuser, and the ring and the tip of the wing may be installed by welding, bonding, painting, or pressing soft rubber.
また、各段の静止流路には図６に示した嵌め合い部（例えば、６１６）が構成され、樹脂製のシール材により段間の漏れの防止と組み立て性の向上を図っている。 In addition, the stationary flow path of each step is formed with a fitting portion (for example, 616) shown in FIG. 6, and a resin sealing material prevents leakage between steps and improves assembly.
なお、電動送風機内部の流れについては、実施例１と同じなので省略する。
In addition, about the flow inside an electric blower, since it is the same as Example 1, it abbreviate | omits.
次に、本発明が対象とする電気掃除機の代表諸元について説明する。本発明に用いられる電動送風機の羽根車外径はおおよそφ４０mm〜φ１２０mmの範囲にあり、羽根出口高さはおおよそ５〜１２mmの範囲にあり、羽根の板厚はおおよそ０.５〜１.５mmの範囲にあり、羽根枚数はおおよそ６〜１３枚の範囲にあり、最高回転数はおおよそ毎分３０、０００〜１００、０００回転の範囲にある。また、電気掃除機の定格消費電力はおおよそ１０００Ｗを超え１５００Ｗ以下の範囲にある。 Next, representative specifications of the vacuum cleaner targeted by the present invention will be described. The impeller outer diameter of the electric blower used in the present invention is approximately in the range of φ40 mm to φ120 mm, the blade outlet height is in the range of approximately 5 to 12 mm, and the blade thickness is approximately in the range of 0.5 to 1.5 mm. The number of blades is in the range of approximately 6 to 13 and the maximum rotational speed is in the range of approximately 30,000 to 100,000 revolutions per minute. Moreover, the rated power consumption of the vacuum cleaner is in the range of more than about 1000 W and less than 1500 W.
なお、本実施の形態例ではシュラウドを有する羽根車を説明したが、シュラウドを有していないオープンタイプの羽根車でもよい。
In the present embodiment, an impeller having a shroud has been described. However, an open type impeller having no shroud may be used.
次に、図７を用いて、最終段（図では、２段目）の羽根車７０１の入口部に注目し，吸込仕事率点と最大電流となる風量時の流れの比較を示す。図７は図２で示した送風機部の一部と風の流れを示し、実線は吸込仕事率点を、点線は最大風量となる風量時の流れを示す。 Next, with reference to FIG. 7, focusing on the inlet portion of the final stage (second stage in the figure) impeller 701, a comparison is made between the suction work rate point and the flow at the time of the air flow at the maximum current. FIG. 7 shows a part of the blower unit shown in FIG. 2 and the flow of the wind, the solid line indicates the suction work point, and the dotted line indicates the flow at the time of the air volume that becomes the maximum air volume.
吸込仕事率点の流れ７０７は、前段の羽根車で昇圧された流れがディフューザを通り、曲がり部で略１８０゜転向され、リターンガイドに流入する。また、リターンガイドへ流入した流れは、リターンガイドの子午面形状に沿うように流れる。なお、リターンガイド出口の流れはリターンガイド内で旋回成分が低減され、マウスリングの曲率部７０４とカラー７０５の形状により、増速され最終段の羽根車７０１内へ流入される。なお、初段羽根車７０３の入口流れは、略軸方向から一様に流入する。一方、最終段の羽根車の入口流れは、リターンガイドにより半径方向内側へ流れが集められる。このため、最終段のマウスリングの曲率部の流れは、動作風量（速度）の影響を受けやすい。本実施例の最終段のマウスリングの曲率部の半径は、約４ｍｍ〜８ｍｍ程度で構成し、初段のマウスリング曲率部６１７の半径に比べて大きくしている。このため、吸込仕事率点での最終段の流れは曲率部ではく離が生じることなく、羽根車７０１内へ流入する。そのため、最終段の軸動力は他の段の羽根車と同等となる。 In the flow 707 at the suction work rate point, the flow boosted by the preceding impeller passes through the diffuser, is turned by approximately 180 ° at the bent portion, and flows into the return guide. Further, the flow that flows into the return guide flows along the meridional shape of the return guide. The flow at the exit of the return guide is reduced in the swirling component in the return guide, and is accelerated by the shape of the curvature portion 704 and the collar 705 of the mouth ring and flows into the final stage impeller 701. Note that the inlet flow of the first stage impeller 703 flows uniformly from the substantially axial direction. On the other hand, the flow at the inlet of the final stage impeller is collected radially inward by the return guide. For this reason, the flow of the curvature part of the last stage mouth ring is easily influenced by the operation air volume (speed). The radius of the curvature portion of the last stage mouth ring of this embodiment is about 4 mm to 8 mm, and is larger than the radius of the first stage mouth ring curvature portion 617. For this reason, the last-stage flow at the suction power point flows into the impeller 701 without separation at the curvature portion. Therefore, the final stage shaft power is equivalent to that of the other stage impellers.
本発明の送風機は高入力化を図る場合、多段送風機であるために、１段あたりの軸動力を小さくできることから、羽根車内の風速を低減でき、摩擦損失の低減による高効率化と，低騒音化の両立が可能となる。さらに、最終段上流のマウスリングの曲率部７０４の曲率半径は、初段のマウスリング曲率部７０２の半径に比べて大きくしているため、吸込仕事率点における最終段の羽根車入口流れを均一化でき、効率向上が図れる。 Since the blower of the present invention is a multi-stage blower for higher input, the shaft power per stage can be reduced, so that the wind speed in the impeller can be reduced, the efficiency is improved by reducing friction loss, and the noise is reduced. It becomes possible to achieve both. Furthermore, since the curvature radius of the curvature part 704 of the mouth ring upstream of the final stage is larger than the radius of the mouth ring curvature part 702 of the first stage, the final stage impeller inlet flow at the suction work point is made uniform. Can improve efficiency.
一方、最大電流時の風量は吸込仕事率点の風量に比べて約１．５倍と大きい。マウスリングの曲率部において、最大電流となる風量時の流れ７０８は、羽根車内部に向かう増速流れであり、吸込仕事率点に比べて流れが速い。このため、マウスリングの曲率部の流れは、曲率部の形状に流れが沿うことが出来ず、羽根車の前縁７０６において、軸方向に速度差が生じる。すなわち、最終段における最大電流時の羽根車前縁７０６の流れは、前縁のシュラウド側７０９が遅く、ハブ側７１０が速くなり偏った流れとなり、羽根車内の速度が不均一となる。このため、最大電流となる風量時の最終段の羽根車は、他の段の羽根車に比べて軸動力が小さくなる。 On the other hand, the air volume at the maximum current is about 1.5 times larger than the air volume at the suction power point. In the curvature part of the mouth ring, the flow 708 at the time of the air volume that becomes the maximum current is a speed increasing flow toward the inside of the impeller, and the flow is faster than the suction work point. For this reason, the flow of the curvature portion of the mouth ring cannot follow the shape of the curvature portion, and a speed difference occurs in the axial direction at the front edge 706 of the impeller. In other words, the flow of the impeller front edge 706 at the maximum current in the final stage is a slow flow on the shroud side 709 of the front edge and a high speed on the hub side 710, resulting in uneven speed in the impeller. For this reason, the last stage impeller at the time of the air volume which becomes the maximum current has a smaller shaft power than the other stage impellers.
図８に電流値を向上させ消費電力を高めた場合の、従来技術と本発明の構成による電流や空気力学的動力の特性の比較を示す。図８(a)に示した従来技術は、本実施例で説明したように動作風量に応じて最終段の羽根車の流れを積極的に変化させる構成（例えば、最終段のマウスリングの曲率部の半径は、初段のマウスリング曲率部の半径に比べて大きくした構成）を有していない。このため、消費電力を高めた場合、最大電流となる風量時の軸動力が大きくなる。すなわち、最大電流が１５Ａを超えてしまうため、吸込仕事率点の高入力化ができず、吸込仕事率の向上が困難である。 FIG. 8 shows a comparison of characteristics of current and aerodynamic power according to the configuration of the prior art and the present invention when the current value is improved and the power consumption is increased. The prior art shown in FIG. 8 (a) has a configuration in which the flow of the impeller at the final stage is actively changed according to the operating air volume as described in this embodiment (for example, the curvature portion of the mouth ring at the final stage). Is not larger than the radius of the first stage mouth ring curvature portion. For this reason, when power consumption is raised, the shaft power at the time of the air volume which becomes the maximum electric current becomes large. That is, since the maximum current exceeds 15 A, it is not possible to increase the suction power point and it is difficult to improve the suction power.
一方、図８(b)に示した本発明は、動作風量に応じて最終段の羽根車の流れを積極的に変化させる構成を持っているため、最大電流となる風量時の軸動力が低下し、最大電流が低下する。すなわち、吸込仕事率点の電流と最大電流との差を小さくできる。このため、本発明は、吸込仕事率点の高入力と、最大電流の低減が両立でき、吸込仕事率の向上が図れる。
On the other hand, the present invention shown in FIG. 8 (b) has a configuration in which the flow of the impeller at the final stage is positively changed according to the operating air volume, so that the shaft power at the time of the air volume at which the maximum current is reduced is reduced. However, the maximum current decreases. That is, the difference between the current at the suction power point and the maximum current can be reduced. For this reason, the present invention can achieve both high input of the suction power point and reduction of the maximum current, and can improve the suction power.
また、異なる電気環境においても同様な効果がある。例えば、使用電圧１１０Vの掃除機の吸込仕事率を消費電力で向上させる場合、電源コードの電流上限値（１５Ａ未満）を満足するため、最大電流の低減が必要である。そのため、最大電流を増加させることなく、吸込仕事率点の電流を増加させ、吸込仕事率の向上を図るには、実施例１に示した構成にすればよい。
Also, the same effect can be obtained in different electrical environments. For example, when the suction power of a cleaner with a working voltage of 110 V is improved with power consumption, the maximum current must be reduced to satisfy the current upper limit (less than 15 A) of the power cord. Therefore, in order to increase the current at the suction power point and increase the suction power without increasing the maximum current, the configuration shown in the first embodiment may be used.
実施例１と基本的な構成は同じであるので同一要素については同一符号を付してその説明を省略する。次に、図９を用いて、羽根車９００の形状について説明する。ここでは、図２中の送風機２０１に注目して記載し、送風機を９００とし説明する。 Since the basic configuration is the same as that of the first embodiment, the same elements are denoted by the same reference numerals and the description thereof is omitted. Next, the shape of the impeller 900 will be described with reference to FIG. Here, the blower 201 in FIG. 2 will be noted and described, and the blower will be described as 900.
送風機９００は、図２の送風機部分と同じように、シュラウドを有する２つの羽根車９０１、９０２を持つ２段送風機を図示している。送風機の基本的な構成は実施例１と同じなので省略する。 The blower 900 illustrates a two-stage blower having two impellers 901 and 902 having shrouds, similar to the blower portion of FIG. Since the basic configuration of the blower is the same as that of the first embodiment, a description thereof will be omitted.
図９のディフューザ９０５の子午面形状（回転軸心を含む平面）は、シュラウド側のリング９０３と仕切り板９０６で構成されている。また、曲がり部９０７の子午面形状は、ファンケーシング９０４とマウスリング９１０から構成され，緩やかな形状で半径方向の外向きに向いた流れを内向きへ略１８０゜転向させる。なお、曲がり部９０７の子午面形状は、リング９０３とマウスリング９１０から形成されていてもよい。リターンガイド９０８は仕切り板９０６と一体で構成されている。最終段のリターンガイドのシュラウド面を形成するマウスリング９１０は、羽根車入口に流れを案内する曲率部９０９を有している。また、曲率部の周辺かつリターンガイドのシュラウド面のうち、最も軸方向上流に位置する場所に、流れのはく離を誘発する凸部９１７を設けている。この凸部は、周方向に略均一の高さで軸方向に構成されている。ここで、凸部は段差でも凹部でもよい。また、凸部の高さは樹脂成型品の場合、型の合わせ面に生じるバリの高さ以上で構成されている。最終段の羽根車下流に設けたディフューザ９１２は、シュラウド側のリング９１１と、ディフューザ翼と仕切り板９１５から構成されている。また、ディフューザの下流には曲がり部９１３と、他の段と同様にリターンガイド９１４が設置されている。 The meridian surface shape (plane including the rotation axis) of the diffuser 905 in FIG. 9 includes a shroud-side ring 903 and a partition plate 906. Further, the meridional shape of the bent portion 907 is composed of a fan casing 904 and a mouth ring 910, and turns the flow outward in the radial direction in a gentle shape by approximately 180 ° inward. The meridional shape of the bent portion 907 may be formed from a ring 903 and a mouth ring 910. The return guide 908 is configured integrally with the partition plate 906. The mouth ring 910 that forms the shroud surface of the final-stage return guide has a curvature portion 909 that guides the flow to the impeller inlet. In addition, a convex portion 917 that induces flow separation is provided at a location that is located in the vicinity of the curvature portion and on the most shroud surface of the return guide in the axial direction upstream. This convex part is comprised by the axial direction by the substantially uniform height in the circumferential direction. Here, the convex portion may be a step or a concave portion. Further, in the case of a resin molded product, the height of the convex portion is configured to be equal to or higher than the height of the burr generated on the mating surface of the mold. The diffuser 912 provided downstream of the final stage impeller is composed of a shroud-side ring 911, a diffuser blade, and a partition plate 915. Further, a bent portion 913 and a return guide 914 are installed on the downstream side of the diffuser like the other stages.
なお、前記マウスリング９１０は、最終段のディフューザのリング９１１と軸芯を出すために、嵌め合い部９１６を有している。また、前記マウスリング９１０は、最終段のディフューザのリング９１１とネジ等で固定され、部品間の合わせ面に樹脂製のシール材が設けられ、ディフューザ流路の漏れを防止している。 The mouth ring 910 has a fitting portion 916 in order to align with the ring 911 of the final stage diffuser. Further, the mouth ring 910 is fixed to the ring 911 of the final stage diffuser with a screw or the like, and a resin sealing material is provided on the mating surface between the components to prevent leakage of the diffuser flow path.
初段の静止流路の部品構成は（ディフューザ９０５、曲がり部９０７、リターンガイド９０８を含む）は、ディフューザ９０５、仕切り板９０６、リターンガイド９０８が例えば、樹脂製の一体成型品で構成され、これらを挟み込むように軸方向の上流側にリング９０３、下流側にマウスリング９１０が溶着もしくは、接着されていている。なお、リング９０３は、ディフューザの翼と接しており，リングと翼の先端は溶着や接着もしくは塗装、もしくはやわらかいゴムをかえして押し付けて設置されてもよい。 The component structure of the first-stage static flow path (including the diffuser 905, the bent portion 907, and the return guide 908) is configured such that the diffuser 905, the partition plate 906, and the return guide 908 are formed of, for example, a resin integrally molded product. A ring 903 is welded or bonded to the upstream side in the axial direction and a mouth ring 910 is welded to the downstream side so as to be sandwiched. The ring 903 may be in contact with the wing of the diffuser, and the ring and the tip of the wing may be installed by welding, bonding, painting, or pressing soft rubber instead.
また、各段の静止流路には図９に示した嵌め合い部（例えば、９１６）が構成され、樹脂製のシール材により段間の漏れの防止と組み立て性の向上を図っている。 Further, the stationary flow path of each stage is formed with a fitting portion (for example, 916) shown in FIG. 9, and a resin sealing material prevents leakage between stages and improves the assemblability.
なお、電動送風機内部の流れについては、実施例１と同じなので省略する。
In addition, about the flow inside an electric blower, since it is the same as that of Example 1, it abbreviate | omits.
次に、本発明が対象とする電気掃除機の代表諸元について説明する。本発明に用いられる電動送風機の羽根車外径はおおよそφ４０mm〜φ１２０mmの範囲にあり、羽根出口高さはおおよそ５〜１２mmの範囲にあり、羽根の板厚はおおよそ０.５〜１.５mmの範囲にあり、羽根枚数はおおよそ６〜１３枚の範囲にあり、最高回転数はおおよそ毎分３０、０００〜１００、０００回転の範囲にある。また、電気掃除機の定格消費電力はおおよそ１０００Ｗを超え１５００Ｗ以下の範囲にある。 Next, representative specifications of the vacuum cleaner targeted by the present invention will be described. The impeller outer diameter of the electric blower used in the present invention is approximately in the range of φ40 mm to φ120 mm, the blade outlet height is in the range of approximately 5 to 12 mm, and the blade thickness is approximately in the range of 0.5 to 1.5 mm. The number of blades is in the range of approximately 6 to 13 and the maximum rotational speed is in the range of approximately 30,000 to 100,000 revolutions per minute. Moreover, the rated power consumption of the vacuum cleaner is in the range of more than about 1000 W and less than 1500 W.
なお、本実施の形態例ではシュラウドを有する羽根車を説明したが、シュラウドを有していないオープンタイプの羽根車でもよい。
In the present embodiment, an impeller having a shroud has been described. However, an open type impeller having no shroud may be used.
次に、図１０を用いて、最終段（図では、２段目）の羽根車１００１の入口部に注目し，吸込仕事率点と最大電流となる風量時の流れの比較を示す。図１０は図２で示した送風機部の一部と風の流れを示し、実線は吸込仕事率点を、点線は最大風量となる風量時の流れを示す。 Next, using FIG. 10, focusing on the inlet portion of the impeller 1001 at the final stage (second stage in the figure), a comparison is made between the suction power point and the flow at the time of the air volume at which the maximum current is reached. FIG. 10 shows a part of the blower unit shown in FIG. 2 and the flow of the wind, the solid line indicates the suction work point, and the dotted line indicates the flow at the time of the air volume that becomes the maximum air volume.
吸込仕事率点の流れ１００７は、前段の羽根車で昇圧された流れがディフューザを通り、曲がり部で略１８０゜転向され、リターンガイドに流入する。また、リターンガイドへ流入した流れは、リターンガイドの子午面形状に沿うように流れる。なお、リターンガイド出口の流れはリターンガイド内で旋回成分が低減され、最終段に設けられた凸部１０１１を通る。曲率部の流れは、マウスリングの曲率部１００４とカラー回転軸１００５の形状により、増速され最終段の羽根車１００１内へ流入される。なお、最終段に設けられた凸部の流れは速度に応じたはく離域１００１、１００２が生じる。はく離した流れは風量が小さいと曲率部１００４で再付着するが、風量が大きい場合は曲率部で再付着することができず、最終段の羽根車１００１へと流入する。 In the flow 1007 at the suction work rate point, the flow increased in pressure by the preceding impeller passes through the diffuser, is turned by approximately 180 ° at the bent portion, and flows into the return guide. Further, the flow that flows into the return guide flows along the meridional shape of the return guide. The flow of the return guide exit is reduced in the swirling component in the return guide and passes through the convex portion 1011 provided in the final stage. The flow of the curvature portion is increased by the shape of the curvature portion 1004 of the mouth ring and the color rotating shaft 1005 and flows into the final stage impeller 1001. In addition, the flow of the convex part provided in the last stage produces the separation areas 1001 and 1002 corresponding to the speed. The separated flow is reattached at the curvature portion 1004 when the air volume is small, but cannot be reattached at the curvature portion when the air volume is large and flows into the impeller 1001 at the final stage.
このため、吸込仕事率点における最終段の曲率部流れは、凸部により小さなはく離１０１１が生じるが、曲率部で再付着し羽根車１００１内へ流入する。そのため、最終段の軸動力は他の段の羽根車と同等となる。 For this reason, the curvature portion flow of the final stage at the suction power point is caused by a small separation 1011 due to the convex portion, but reattaches at the curvature portion and flows into the impeller 1001. Therefore, the final stage shaft power is equivalent to that of the other stage impellers.
本発明の送風機は高入力化を図る場合、多段送風機であるために、１段あたりの軸動力を小さくできることから、羽根車内の風速を低減でき、摩擦損失の低減による高効率化と，低騒音化の両立が可能となる。 Since the blower of the present invention is a multi-stage blower for higher input, the shaft power per stage can be reduced, so that the wind speed in the impeller can be reduced, the efficiency is improved by reducing friction loss, and the noise is reduced. It becomes possible to achieve both.
一方、最大電流時の風量は吸込仕事率点の風量に比べて約１．５倍と大きい。マウスリングの曲率部において、最大電流となる風量時の流れ１１０８は、羽根車内部に向かう増速流れであり、吸込仕事率点に比べて流れが速い。そのため、最大電流となる風量時のマウスリングの曲率部の流れ１００８は、凸部で生じたはく離１０１３が大きいため、曲率部で再付着出来ず、羽根車の前縁１００６において、軸方向に速度差が生じる。すなわち、最終段における最大電流時の羽根車前縁１００６部の流れは、前縁のシュラウド側１００９が遅く、ハブ側１０１０が速くなり偏った流れとなり、羽根車内の速度が不均一となる。このため、最大電流となる風量時の最終段の羽根車は、他の段の羽根車に比べて軸動力が小さくなる。 On the other hand, the air volume at the maximum current is about 1.5 times larger than the air volume at the suction power point. In the curvature portion of the mouth ring, the flow 1108 at the time of the air flow that becomes the maximum current is a speed increasing flow toward the inside of the impeller, and the flow is faster than the suction work point. Therefore, the flow 1008 of the curvature portion of the mouth ring at the time of the air flow at which the maximum current is generated cannot be reattached at the curvature portion because the separation 1013 generated at the convex portion is large, and the velocity in the axial direction at the leading edge 1006 of the impeller There is a difference. That is, the flow of the impeller leading edge 1006 at the maximum current in the final stage is a slow flow on the shroud side 1009 of the front edge and a high speed on the hub side 1010, resulting in uneven speed in the impeller. For this reason, the last stage impeller at the time of the air volume which becomes the maximum current has a smaller shaft power than the other stage impellers.
図１１に電流値を向上させ消費電力を高めた場合の、従来技術と本発明の構成による電流や空気力学的動力の特性の比較を示す。図１１(a)に示した従来技術は、本実施例で説明したように動作風量に応じて最終段の羽根車の流れを積極的に変化させる構成（例えば、最終段のマウスリングの曲率部にはく離を誘発する凸部を設けた構成）を有していない。このため、消費電力を高めた場合、最大電流となる風量時の軸動力が大きくなる。すなわち、最大電流が１５Ａを超えてしまうため、吸込仕事率点の高入力化ができず、吸込仕事率の向上が困難である。 FIG. 11 shows a comparison of characteristics of current and aerodynamic power according to the configuration of the prior art and the present invention when the current value is improved and the power consumption is increased. The prior art shown in FIG. 11A has a configuration in which the flow of the impeller at the final stage is positively changed according to the operating air volume as described in the present embodiment (for example, the curvature portion of the mouth ring at the final stage. It does not have a structure provided with a convex portion that induces peeling. For this reason, when power consumption is raised, the shaft power at the time of the air volume which becomes the maximum electric current becomes large. That is, since the maximum current exceeds 15 A, it is not possible to increase the suction power point and it is difficult to improve the suction power.
一方、図１１(b)に示した本発明は、動作風量に応じて最終段の羽根車の流れを積極的に変化させる構成を持っているため、最大電流となる風量時の軸動力が低下し、最大電流が低下する。すなわち、吸込仕事率点の電流と最大電流との差を小さくできる。このため、本発明は、吸込仕事率点の高入力と、最大電流の低減が両立でき、吸込仕事率の向上が図れる。
On the other hand, the present invention shown in FIG. 11 (b) has a configuration in which the flow of the impeller at the final stage is actively changed according to the operating air volume, so that the shaft power at the time of the air volume at which the maximum current is reduced is reduced. However, the maximum current decreases. That is, the difference between the current at the suction power point and the maximum current can be reduced. For this reason, the present invention can achieve both high input of the suction power point and reduction of the maximum current, and can improve the suction power.
また、異なる電気環境においても同様な効果がある。例えば、使用電圧１１０Vの掃除機の吸込仕事率を消費電力で向上させる場合、電源コードの電流上限値（１５Ａ未満）を満足するため、最大電流の低減が必要である。そのため、最大電流を増加させることなく、吸込仕事率点の電流を増加させ、吸込仕事率の向上を図るには、実施例１に示した構成にすればよい。
Also, the same effect can be obtained in different electrical environments. For example, when the suction power of a cleaner with a working voltage of 110 V is improved with power consumption, the maximum current must be reduced to satisfy the current upper limit (less than 15 A) of the power cord. Therefore, in order to increase the current at the suction power point and increase the suction power without increasing the maximum current, the configuration shown in the first embodiment may be used.
１００ 電気掃除機本体
１０１ ホース継ぎ手
１０２ 集塵室
１０３ 紙パック
１０４ フィルタ部
１０５ モータ室
１０６、２００ 電動送風機
１０７ 防振ゴム
１０８ 送風機入口
１０９ 送風機出口
１１０ コードリール
１１１ 車輪
１１２ 制御回路
２０１、４００、６００、９００ 送風機
２０２ 電動機
２０３ ハウジング
２０４ エンドブラケット
２０５ 回転軸
２０６ ロータ
２０７ ステータ
２０８ ブラシ
２０９ コンミテータ
２１０、２２０、４０１、６０１、６０２、７０１、７０３、９０１、９０２、１００１、
１００２ 羽根車
２１１、２２１、６０５、６１２、９０５、９１２ ディフューザ
２１２、２２２、６０６、６１５、９０６、９１５ 仕切り板
２１３、２２３、６０８、６１４、９０８、９１４ リターンガイド
２１４、６０４、９０４ ファンケーシング
２１５、２２９ 目玉部
２１６、２３６ シール材
２１７ 電動送風機入口
２１８ 軸受
２１９、２２５、６０３、６１１、９０３、９１１ リング
２２４、６１０、９１０ マウスリング
２２６、４１０、７１０、９１０、１０１０ 羽根車のハブ面
２２７、４０４、６０９、６１７、７０２、７０４、９０９、１００４ 曲率部
２２８、６１６、９１６ 嵌め合い部
２３０、４０９、７０９、１００９ 羽根車のシュラウド
２３１、４０５、７０５、１００５ カラー
２３２、２３３、６０７、６１３、９０７、９１３ 曲がり部
２３４ リターンガイドの子午面形状の軸方向最下流の面
２３５ 羽根車背面の突起
２３６ 羽根車背面のシール構造
３００ 電流と吸込仕事率の変化
４００、７００、１０００ 吸込仕事率点と最大電流となる風量時の最終段羽根車入口部流れの比較
４０２ リターンガイドの子午面形状のハブ面
４０３ リターンガイドの子午面形状のシュラウド面
４０６、７０６、１００６ 前縁
４０７、７０７、１００７ 吸込仕事率点の最終段入口部の流れ
４０８、７０８、１００８ 最大電流となる風量時の最終段入口部の流れ
５００、８００、１１００ 電動送風機効率と電流と吸込仕事率の変化
９１７、１０１１ マウスリングの曲率部の凸部
１００２、１００３ はく離
DESCRIPTION OF SYMBOLS 100 Vacuum cleaner main body 101 Hose coupling 102 Dust collection chamber 103 Paper pack 104 Filter part 105 Motor chamber 106, 200 Electric blower 107 Anti-vibration rubber 108 Blower inlet 109 Blower outlet 110 Code reel 111 Wheel 112 Control circuit 201, 400, 600, 900 Blower 202 Electric motor 203 Housing 204 End bracket 205 Rotating shaft 206 Rotor 207 Stator 208 Brush 209 Commutators 210, 220, 401, 601, 602, 701, 703, 901, 902, 1001,
1002 Impeller 211, 221, 605, 612, 905, 912 Diffuser 212, 222, 606, 615, 906, 915 Partition plate 213, 223, 608, 614, 908, 914 Return guide 214, 604, 904 Fan casing 215, 229 Eyepiece portion 216, 236 Sealing material 217 Electric blower inlet 218 Bearing 219, 225, 603, 611, 903, 911 Ring 224, 610, 910 Mouth ring 226, 410, 710, 910, 1010 Impeller hub surface 227, 404 , 609, 617, 702, 704, 909, 1004 Curvature part 228, 616, 916 Fitting part 230, 409, 709, 1009 Impeller shroud 231, 405, 705, 1005 Collar 232, 233, 607, 613 , 907, 913 Bend 234 Axis most downstream surface 235 of meridional shape of return guide 235 Protrusion 236 on impeller back surface Seal structure on impeller back surface 300 Current and suction power change 400, 700, 1000 Suction power factor Comparison of the flow at the inlet of the final stage impeller when the air flow is the maximum current 402 The meridian-shaped hub surface 403 of the return guide The meridian-shaped shroud surface 406, 706, 1006 of the return guide The leading edges 407, 707, 1007 Last stage inlet flow 408, 708, 1008 at the power point The last stage inlet flow 500, 800, 1100 at the time of the maximum air flow Changes in the electric fan efficiency, current and suction work rate 917, 1011 Convex parts 1002, 1003 of curvature part
Claims (8)
In an electric blower comprising a hub, an impeller composed of a plurality of blades arranged in the circumferential direction, and an electric motor for rotating the impeller, wherein the impeller is formed in a plurality of stages in the axial direction of the electric motor. An electric cleaning characterized in that both the shroud surface and the hub surface forming the meridional shape of the return guide upstream of the vehicle are gently inclined toward the upstream side in the axial direction of the rotating shaft as it goes inward in the radial direction. Machine electric blower.
A hub, an impeller including a plurality of blades arranged in a circumferential direction, and an electric motor that rotates the impeller, the impeller is formed in a plurality of stages in the axial direction of the electric motor, and upstream of the impeller, In the electric blower in which the mouth ring having the curvature part is formed near the center part of the impeller, the radius of the curvature part of the mouth ring upstream of the final stage impeller is compared with the curvature radius of the mauling provided in the first stage impeller. An electric blower of a vacuum cleaner characterized by being enlarged.
In an electric blower comprising a hub, an impeller composed of a plurality of blades arranged in the circumferential direction, and an electric motor for rotating the impeller, wherein the impeller is formed in a plurality of stages in the axial direction of the electric motor. An electric blower for a vacuum cleaner, characterized in that a convex portion for inducing separation is formed in a location that is located at the most upstream in the axial direction of the mouth ring upstream of the vehicle and in the vicinity of the curvature portion that guides the flow to the main part of the impeller .
最終段の羽根車の目玉部を、上流のリターンガイドの子午面形状の軸方向最下面に比べ、軸方向の上流側に配置したことを特徴とする電気掃除機の電動送風機。
In the electric blower of the household vacuum cleaner according to any one of claims 1 to 3,
An electric blower for a vacuum cleaner, characterized in that the eyeball portion of the impeller at the final stage is arranged on the upstream side in the axial direction as compared with the axially lowermost surface of the meridional shape of the upstream return guide.
回転軸と同軸のカラーを有し、前記カラーは羽根車内部と軸方向に重なる部分を有し、羽根車のハブ面に向かうにつれカラーの外径を緩やかに大きくしたことを特徴とする電気掃除機の電動送風機。
In the electric blower of the vacuum cleaner according to any one of claims 1 to 3,
An electric cleaning characterized by having a collar coaxial with the rotating shaft, the collar having a portion overlapping the inside of the impeller in the axial direction, and gradually increasing the outer diameter of the collar toward the hub surface of the impeller. Machine electric blower.
羽根車を構成する部位が回転軸の軸方向にシール材と概略接触した３つ以上のシール構造を有したことを特徴とする電気掃除機の電動送風機。
In the electric blower of the vacuum cleaner according to any one of claims 1 to 3,
An electric blower for a vacuum cleaner, wherein a portion constituting the impeller has three or more seal structures in which the seal member is substantially in contact with the seal material in the axial direction of the rotation shaft.
初段の静止流路はディフューザ翼と仕切り板とリターンガイドが一体で成型され、リング、マウスリングの３つの部品から構成されていることを特徴とする電気掃除機の電動送風機。
In the electric blower of the vacuum cleaner according to any one of claims 1 to 3,
An electric blower for a vacuum cleaner, characterized in that a first stationary flow path is formed by integrally forming a diffuser blade, a partition plate, and a return guide, and is composed of a ring and a mouth ring.
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| JP2015001232A JP6553360B2 (en) | 2015-01-07 | 2015-01-07 | Electric blower and vacuum cleaner equipped with the same |
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| Application Number | Priority Date | Filing Date | Title |
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| JP2015001232A JP6553360B2 (en) | 2015-01-07 | 2015-01-07 | Electric blower and vacuum cleaner equipped with the same |
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| Publication Number | Publication Date |
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| JP2016125437A true JP2016125437A (en) | 2016-07-11 |
| JP6553360B2 JP6553360B2 (en) | 2019-07-31 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP4212733A4 (en) * | 2021-11-30 | 2023-08-23 | Jiangsu Midea Cleaning Appliances Co., Ltd. | Fan assembly and vacuum cleaner having same |
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