JP6942242B2 - Axial blades and blowers - Google Patents

Axial blades and blowers Download PDF

Info

Publication number
JP6942242B2
JP6942242B2 JP2020508715A JP2020508715A JP6942242B2 JP 6942242 B2 JP6942242 B2 JP 6942242B2 JP 2020508715 A JP2020508715 A JP 2020508715A JP 2020508715 A JP2020508715 A JP 2020508715A JP 6942242 B2 JP6942242 B2 JP 6942242B2
Authority
JP
Japan
Prior art keywords
partition plate
boss
hub
axial flow
space
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
JP2020508715A
Other languages
Japanese (ja)
Other versions
JPWO2019186910A1 (en
Inventor
雄一 安田
雄一 安田
晃史 藤田
晃史 藤田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Publication of JPWO2019186910A1 publication Critical patent/JPWO2019186910A1/en
Application granted granted Critical
Publication of JP6942242B2 publication Critical patent/JP6942242B2/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
    • F04D29/329—Details of the hub
    • 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
    • F04D29/32—Rotors specially for elastic fluids for axial flow pumps
    • F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
    • 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
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • 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
    • 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid 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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/663—Sound attenuation
    • F04D29/665—Sound attenuation by means of resonance chambers or interference
    • 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
    • F05D2210/00—Working fluids
    • F05D2210/10—Kind or type
    • F05D2210/12—Kind or type gaseous, i.e. compressible
    • 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
    • F05D2240/00—Components
    • F05D2240/20—Rotors
    • 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
    • F05D2260/00—Function
    • F05D2260/96—Preventing, counteracting or reducing vibration or noise
    • F05D2260/963—Preventing, counteracting or reducing vibration or noise by Helmholtz resonators

Landscapes

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

Description

本発明は、軸流羽根及びこれを有する送風機に関する。 The present invention relates to an axial flow blade and a blower having the axial flow blade.

事務所又はリビングといった箇所に設置され、電動機により羽根を回転させて風を吹き送る送風機において、電動機と羽根とを結合する羽根中央部は、特許文献１に開示されるように、電動機のシャフトが貫通されるボスと、一端が開口した円筒形状であり翼が配置されるハブとで構成され、電動機の羽根側の面とハブとで囲まれる空間が形成される構造となっていた。 In a blower installed in a place such as an office or a living room where the blades are rotated by an electric motor to blow air, the central portion of the blades connecting the electric motor and the blades has a shaft of the electric motor as disclosed in Patent Document 1. It was composed of a boss to be penetrated and a hub having a cylindrical shape with one end open and where wings were arranged, and had a structure in which a space surrounded by a surface on the blade side of the motor and the hub was formed.

特開平５−０１８３９８号公報Japanese Unexamined Patent Publication No. 5-018398

上記構造の送風機においては、電動機と羽根のハブとによって囲まれた空間には、気柱共鳴又はヘルムホルツ共鳴など、空間の寸法によって決まる周波数で共鳴現象が発生する。共鳴の周波数が電動機のベアリング音などの周波数と一致した場合には、音が増幅され、運転騒音となる。共鳴の周波数を電動機のベアリング音などの周波数とずらして音の増幅を抑えるためには、羽根のハブ内の空間寸法を変更する必要があるが、要求性能への影響から容易に変更できないことがある。 In the blower having the above structure, a resonance phenomenon occurs in the space surrounded by the motor and the hub of the blade at a frequency determined by the dimension of the space, such as air column resonance or Helmholtz resonance. When the resonance frequency matches the frequency of the bearing sound of the motor or the like, the sound is amplified and becomes operating noise. In order to shift the resonance frequency from the frequency of the bearing sound of the motor and suppress the sound amplification, it is necessary to change the spatial dimension in the hub of the blade, but it cannot be easily changed due to the influence on the required performance. be.

このように、電動機の羽根側の面とハブとで囲まれる空間が形成される構造を有する送風機は、共鳴による運転音の増大を防止することが難しかった。 As described above, it is difficult for a blower having a structure in which a space surrounded by a surface on the blade side of the motor and a hub is formed to prevent an increase in operating noise due to resonance.

本発明は、これを鑑みてなされたものであって、電動機の羽根側の面とハブとで囲まれる空間が形成される構造を有し、運転音の増大を容易に防止できる送風機を得ることを目的とする。 The present invention has been made in view of this, and obtains a blower having a structure in which a space surrounded by a surface on the blade side of the motor and a hub is formed, and an increase in operating noise can be easily prevented. With the goal.

上述した課題を解決し、目的を達成するために、本発明は、回転軸を中心にシャフトを回転させる電動機のシャフトが貫通されるボスを備える。本発明は、電動機側が開口した円筒形状であって、ボスと同軸でありボスの周囲を囲うハブを備える。本発明は、ハブの内部に設置されて、ハブの内部の空間を二つ以上に隔てる仕切り板を備える。 In order to solve the above-mentioned problems and achieve the object, the present invention includes a boss through which the shaft of the motor that rotates the shaft around the rotation shaft is penetrated. The present invention includes a hub which has a cylindrical shape with an opening on the motor side, is coaxial with the boss, and surrounds the boss. The present invention includes a partition plate that is installed inside the hub and separates the space inside the hub into two or more.

本発明に係る送風機は、電動機の羽根側の面とハブとで囲まれる空間が形成される構造を有し、共鳴による運転音の増大を容易に防止できるという効果を奏する。 The blower according to the present invention has a structure in which a space surrounded by a surface on the blade side of the motor and a hub is formed, and has an effect that an increase in operating noise due to resonance can be easily prevented.

本発明の実施の形態１に係る軸流羽根を用いた送風機であるサーキュレータファンの斜視図Perspective view of a circulator fan which is a blower using an axial flow blade according to the first embodiment of the present invention. 実施の形態１に係るサーキュレータファンの側断面図Side sectional view of the circulator fan according to the first embodiment 実施の形態１に係るサーキュレータファンの軸流羽根の部分を拡大した部分断面図Enlarged partial cross-sectional view of the axial flow blade of the circulator fan according to the first embodiment. 実施の形態１に係るサーキュレータファンの電動機と羽根の取付構造の分解斜視図An exploded perspective view of the mounting structure of the motor and blades of the circulator fan according to the first embodiment. 実施の形態１に係るサーキュレータファンのハブ内部の側断面拡大図Enlarged view of the side cross section inside the hub of the circulator fan according to the first embodiment. 本発明の実施の形態２に係るサーキュレータファンのハブ内部の側断面拡大図Enlarged view of the inside of the hub of the circulator fan according to the second embodiment of the present invention. 本発明の実施の形態３に係るサーキュレータファンのハブ内部の側断面拡大図Enlarged view of the inside of the hub of the circulator fan according to the third embodiment of the present invention. 実施の形態３に係るサーキュレータファンのハブ内部を区切る仕切り板の斜視図Perspective view of a partition plate that divides the inside of the hub of the circulator fan according to the third embodiment.

以下に、本発明の実施の形態に係る軸流羽根及び送風機を図面に基づいて詳細に説明する。なお、この実施の形態によりこの発明が限定されるものではない。 Hereinafter, the axial flow blade and the blower according to the embodiment of the present invention will be described in detail with reference to the drawings. The present invention is not limited to this embodiment.

実施の形態１．
図１は、本発明の実施の形態１に係る軸流羽根を用いた送風機であるサーキュレータファンの斜視図である。図２は、実施の形態１に係るサーキュレータファンの側断面図である。図１及び図２に示すように、送風機であるサーキュレータファン１は、床面設置用のスタンド２と、上下方向に旋回可能にスタンド２に保持された本体フレーム３とを有する。本体フレーム３には、電動機１００と、電動機１００に通電される電圧を調節して駆動速度を変更する電気ユニット４とが取り付けられており、電源コード５を介して外部電源が供給される。電動機１００のシャフト１０１には、軸流羽根２００が取り付けられている。電動機１００が駆動されることで軸流羽根２００が回転し、サーキュレータファン１は、前方に風を吹き送る。Embodiment 1.
FIG. 1 is a perspective view of a circulator fan which is a blower using an axial flow blade according to a first embodiment of the present invention. FIG. 2 is a side sectional view of the circulator fan according to the first embodiment. As shown in FIGS. 1 and 2, the circulator fan 1 which is a blower has a stand 2 for floor installation and a main body frame 3 which is held by the stand 2 so as to be swivel in the vertical direction. An electric motor 100 and an electric unit 4 that adjusts the voltage applied to the electric motor 100 to change the driving speed are attached to the main body frame 3, and external power is supplied via the power cord 5. An axial flow blade 200 is attached to the shaft 101 of the electric motor 100. The axial flow blade 200 is rotated by driving the electric motor 100, and the circulator fan 1 blows wind forward.

図３は、実施の形態１に係るサーキュレータファンの軸流羽根の部分を拡大した部分断面図である。なお、図３は、電動機１００は側面を図示し、軸流羽根２００は断面を示している。図４は、実施の形態１に係るサーキュレータファンの電動機と羽根の取付構造の分解斜視図である。図３及び図４に示すように、軸流羽根２００の中央部２０１は、電動機１００のシャフト１０１が嵌合するボス穴２０３が形成されたボス２０２と、翼２０４が配置されるハブ２０５とで構成される。ハブ２０５は、一端が開口した円筒形状であり、中心軸はボス２０２の中心軸と同軸である。軸流羽根２００がシャフト１０１に取り付けられた状態では、ハブ２０５の開口端２０６は電動機１００側を向く。また、ボス２０２の端面２０７は開口端２０６よりもハブ２０５の内側に入り込んでいる。 FIG. 3 is an enlarged partial cross-sectional view of a portion of the axial flow blade of the circulator fan according to the first embodiment. In FIG. 3, the electric motor 100 shows a side surface, and the axial flow blade 200 shows a cross section. FIG. 4 is an exploded perspective view of the mounting structure of the electric motor and the blades of the circulator fan according to the first embodiment. As shown in FIGS. 3 and 4, the central portion 201 of the axial flow blade 200 is formed by a boss 202 in which a boss hole 203 into which the shaft 101 of the motor 100 is fitted is formed, and a hub 205 in which the blade 204 is arranged. It is composed. The hub 205 has a cylindrical shape with one end open, and the central axis is coaxial with the central axis of the boss 202. When the axial flow blade 200 is attached to the shaft 101, the opening end 206 of the hub 205 faces the motor 100 side. Further, the end face 207 of the boss 202 enters the inside of the hub 205 with respect to the opening end 206.

一方、電動機１００のシャフト１０１は、先端部１０２と電動機フレーム１０３との間に溝１０４が設けられている。溝１０４には、Ｃリング１０５が係合されている。また、先端部１０２には、Ｄカット形状のねじ部１０７が形成されている。ボス穴２０３にシャフト１０１を通した後に袋ナット１０８をねじ部１０７に締め付けることで、軸流羽根２００がシャフト１０１に固定される。このとき、軸流羽根２００と袋ナット１０８との間には駆動伝達板３００が挟まれ、ボス２０２とＣリング１０５との間には突き当て部となる樹脂ワッシャ１０６と仕切り板４００とが挟まれ、固定される。 On the other hand, the shaft 101 of the motor 100 is provided with a groove 104 between the tip 102 and the motor frame 103. A C ring 105 is engaged with the groove 104. Further, a D-cut shaped screw portion 107 is formed on the tip portion 102. The axial flow blade 200 is fixed to the shaft 101 by tightening the bag nut 108 to the screw portion 107 after passing the shaft 101 through the boss hole 203. At this time, the drive transmission plate 300 is sandwiched between the axial flow blade 200 and the bag nut 108, and the resin washer 106 and the partition plate 400, which are abutting portions, are sandwiched between the boss 202 and the C ring 105. It is fixed.

駆動伝達板３００は、板面３０１の中央に、シャフト１０１の先端部１０２のＤカットと同形状の穴３０２が形成されている。板面３０１の端３０３，３０４には、板面３０１に対し垂直に配置された爪３０５，３０６が設けられている。穴３０２がＤカット形状のねじ部１０７と係合し、爪３０５，３０６がハブ２０５の前面２０５ａに設けられた差込穴２０８，２０９に係合されることで、シャフト１０１の回転が軸流羽根２００に伝達される。 In the drive transmission plate 300, a hole 302 having the same shape as the D-cut of the tip portion 102 of the shaft 101 is formed in the center of the plate surface 301. Claws 305 and 306 arranged perpendicular to the plate surface 301 are provided at the ends 303 and 304 of the plate surface 301. The hole 302 is engaged with the D-cut threaded portion 107, and the claws 305 and 306 are engaged with the insertion holes 208 and 209 provided on the front surface 205a of the hub 205, so that the rotation of the shaft 101 is axially flowed. It is transmitted to the blade 200.

仕切り板４００は、板面４０１の中央にシャフト１０１の直径と同寸法の穴４０２が形成されている。仕切り板４００の外径は、ハブ２０５の内径よりも小さい寸法の形状となっている。 In the partition plate 400, a hole 402 having the same size as the diameter of the shaft 101 is formed in the center of the plate surface 401. The outer diameter of the partition plate 400 is smaller than the inner diameter of the hub 205.

図５は、実施の形態１に係るサーキュレータファンのハブ内部の側断面拡大図である。軸流羽根２００とともに仕切り板４００が電動機１００に組み付けられたとき、仕切り板４００は、ハブ２０５の内部に設置され、図３に示したハブ２０５と電動機１００との間に形成される空間５００を空間５０１と空間５０２とに隔てる。仕切り板４００が空間５００を空間５０１と空間５０２とに隔てることにより、仕切り板４００よりも電動機１００側の空間５０２で共鳴が発生する。仕切り板４００を設置した場合には、共鳴が発生する空間の軸流羽根２００の回転軸方向の寸法は、ハブ２０５の前面２０５ａと仕切り板４００との間の寸法Ａと仕切り板４００と電動機フレーム１０３との間の寸法Ｂとの和であるＡ＋Ｂから仕切り板４００と電動機フレーム１０３との間の寸法であるＢに変化する。また、仕切り板４００を設置した場合には、共鳴が発生する空間の体積は、ハブ２０５の前面２０５ａと仕切り板４００との間の空間５０１の体積Ｖ１と仕切り板４００と電動機フレーム１０３との間の空間５０２の体積Ｖ２との和であるＶ１＋Ｖ２から仕切り板４００と電動機フレーム１０３との間の空間５０２の体積であるＶ２に変化する。仕切り板４００が無い場合には、体積がＶ１＋Ｖ２の空間５００全体において共鳴が発生するため、仕切り板４００が無い場合に、空間５００で増幅される音の周波数は、空間５０２で共鳴が発生する場合に増幅される音の周波数と異なる。したがって、仕切り板４００を設置することにより、気柱共鳴及びヘルムホルツ共鳴の周波数が変化する。また、ハブ２０５の内径と仕切り板４００の外周４０３との間には間隙があるため、空間５０１にもヘルムホルツ共鳴が発生し、共鳴消音の効果が得られる。なお、空間５０１側は、ハブ２０５に回転軸に平行なリブを設けるなどして、仕切り板４００が取り付けられた際に二つ以上の空間が形成される構造でも良い。すなわち、仕切り板４００を設置して電動機１００との間で共鳴が発生する空間の体積を変化させることにより、仕切り板４００が無い場合には増幅される音が、仕切り板４００の設置後には増幅されなくなる。 FIG. 5 is an enlarged side sectional view of the inside of the hub of the circulator fan according to the first embodiment. When the partition plate 400 is assembled to the motor 100 together with the axial flow blade 200, the partition plate 400 is installed inside the hub 205 and provides a space 500 formed between the hub 205 and the motor 100 shown in FIG. It is separated into space 501 and space 502. When the partition plate 400 separates the space 500 into the space 501 and the space 502, resonance occurs in the space 502 on the motor 100 side of the partition plate 400. When the partition plate 400 is installed, the dimensions of the axial flow blade 200 in the space where resonance occurs in the rotation axis direction are the dimension A between the front surface 205a of the hub 205 and the partition plate 400, the partition plate 400, and the motor frame. It changes from A + B, which is the sum of the dimension B between the 103 and the partition plate 400, to B, which is the dimension between the partition plate 400 and the motor frame 103. When the partition plate 400 is installed, the volume of the space where resonance occurs is between the volume V1 of the space 501 between the front surface 205a of the hub 205 and the partition plate 400, the partition plate 400, and the motor frame 103. V1 + V2, which is the sum of the volume V2 of the space 502, changes to V2, which is the volume of the space 502 between the partition plate 400 and the motor frame 103. When there is no partition plate 400, resonance occurs in the entire space 500 having a volume of V1 + V2. Therefore, when there is no partition plate 400, the frequency of the sound amplified in the space 500 is the case where resonance occurs in the space 502. It is different from the frequency of the sound amplified by. Therefore, by installing the partition plate 400, the frequencies of the air column resonance and the Helmholtz resonance change. Further, since there is a gap between the inner diameter of the hub 205 and the outer circumference 403 of the partition plate 400, Helmholtz resonance also occurs in the space 501, and the effect of resonance muffling can be obtained. The space 501 side may have a structure in which two or more spaces are formed when the partition plate 400 is attached, such as by providing a rib parallel to the rotation axis on the hub 205. That is, by installing the partition plate 400 and changing the volume of the space where resonance occurs with the motor 100, the sound amplified in the absence of the partition plate 400 is amplified after the partition plate 400 is installed. Will not be.

実施の形態１に係るサーキュレータファン１は、軸流羽根２００の形状を変更せずに運転騒音の増幅を防止できる。したがって、電動機１００の軸流羽根２００側の面とハブ２０５とで囲まれる空間５００が形成される構造を有するサーキュレータファン１は、共鳴による運転音の増大を容易に防止できる。 The circulator fan 1 according to the first embodiment can prevent the amplification of operating noise without changing the shape of the axial flow blade 200. Therefore, the circulator fan 1 having a structure in which a space 500 surrounded by the surface of the motor 100 on the axial flow blade 200 side and the hub 205 is formed can easily prevent an increase in operating noise due to resonance.

実施の形態２．
図６は、本発明の実施の形態２に係るサーキュレータファンのハブ内部の側断面拡大図である。図６において、実施の形態１と同様の構成要素については同一の符号とし、詳細な説明は省略する。実施の形態２に係るサーキュレータファン１の軸流羽根２００のハブ２０５は、内径側に突出する係合部２１０，２１１，２１２，２１３が形成されている。仕切り板４００は、外周４０３が係合部２１０と係合部２１２との間及び係合部２１１と係合部２１３との間に嵌め込まれることで、軸流羽根２００に固定される。仕切り板４００は、弾性変形によって反らせた状態で係合部２１１と係合部２１３との間に嵌め込むことができるが、他の方法で嵌め込んでもよい。また、仕切り板４００の穴４０２の直径はボス２０２の外径よりも大きく、間隙が設けられている。他の構成要素については、実施の形態１と同様である。 Embodiment 2.
FIG. 6 is an enlarged side sectional view of the inside of the hub of the circulator fan according to the second embodiment of the present invention. In FIG. 6, the same components as those in the first embodiment are designated by the same reference numerals, and detailed description thereof will be omitted. The hub 205 of the axial flow blade 200 of the circulator fan 1 according to the second embodiment is formed with engaging portions 210, 211,212, 213 protruding toward the inner diameter side. The partition plate 400 is fixed to the axial flow blade 200 by fitting the outer peripheral 403 between the engaging portion 210 and the engaging portion 212 and between the engaging portion 211 and the engaging portion 213. The partition plate 400 can be fitted between the engaging portion 211 and the engaging portion 213 in a state of being warped by elastic deformation, but it may be fitted by another method. Further, the diameter of the hole 402 of the partition plate 400 is larger than the outer diameter of the boss 202, and a gap is provided. Other components are the same as those in the first embodiment.

仕切り板４００は、ハブ２０５の内部に設置され、ハブ２０５と電動機１００との間に形成される空間５００を空間５０３と空間５０４とに隔てる。仕切り板４００が空間５００を空間５０３と空間５０４とに隔てることにより、仕切り板４００よりも電動機１００側の空間５０４で共鳴が発生する。仕切り板４００を設置した場合には、共鳴が発生する空間の軸流羽根２００の回転軸方向の寸法は、ハブ２０５の前面２０５ａと仕切り板４００との間の寸法Ｃと仕切り板４００と電動機フレーム１０３との間の寸法Ｄとの和であるＣ＋Ｄから仕切り板４００と電動機フレーム１０３との間の寸法であるＤに変化する。また、仕切り板４００を設置した場合には、共鳴が発生する空間の体積は、ハブ２０５の前面２０５ａと仕切り板４００との間の空間５０３の体積Ｖ３と仕切り板４００と電動機フレーム１０３との間の空間５０４の体積Ｖ４との和であるＶ３＋Ｖ４から仕切り板４００と電動機フレーム１０３との間の空間５０４の体積であるＶ４に変化する。したがって、仕切り板４００を設置することにより、気柱共鳴及びヘルムホルツ共鳴の周波数が変化する。また、ボス２０２の外径と仕切り板４００の穴４０２との間には間隙があるため、空間５０３にもヘルムホルツ共鳴が発生し、共鳴消音の効果が得られる。 The partition plate 400 is installed inside the hub 205, and separates the space 500 formed between the hub 205 and the electric motor 100 into the space 503 and the space 504. When the partition plate 400 separates the space 500 into the space 503 and the space 504, resonance occurs in the space 504 on the motor 100 side of the partition plate 400. When the partition plate 400 is installed, the dimensions of the axial flow blade 200 in the space where resonance occurs in the rotation axis direction are the dimension C between the front surface 205a of the hub 205 and the partition plate 400, the partition plate 400, and the motor frame. It changes from C + D, which is the sum of the dimension D between the 103 and the partition plate 400, to D, which is the dimension between the partition plate 400 and the motor frame 103. When the partition plate 400 is installed, the volume of the space where resonance occurs is between the volume V3 of the space 503 between the front surface 205a of the hub 205 and the partition plate 400, the partition plate 400, and the motor frame 103. V3 + V4, which is the sum of the volume of the space 504 and V4, is changed to V4, which is the volume of the space 504 between the partition plate 400 and the motor frame 103. Therefore, by installing the partition plate 400, the frequencies of the air column resonance and the Helmholtz resonance change. Further, since there is a gap between the outer diameter of the boss 202 and the hole 402 of the partition plate 400, Helmholtz resonance also occurs in the space 503, and the effect of resonance muffling can be obtained.

実施の形態２に係るサーキュレータファン１は、軸流羽根２００の形状を変更せずに運転騒音の増幅を防止できる。したがって、電動機１００の軸流羽根２００側の面とハブ２０５とで囲まれる空間５００が形成される構造を有するサーキュレータファン１は、共鳴による運転音の増大を容易に防止できる。 The circulator fan 1 according to the second embodiment can prevent the amplification of operating noise without changing the shape of the axial flow blade 200. Therefore, the circulator fan 1 having a structure in which a space 500 surrounded by the surface of the motor 100 on the axial flow blade 200 side and the hub 205 is formed can easily prevent an increase in operating noise due to resonance.

実施の形態３．
図７は、本発明の実施の形態３に係るサーキュレータファンのハブ内部の側断面拡大図である。図８は、実施の形態３に係るサーキュレータファンのハブ内部を区切る仕切り板の斜視図である。図７及び図８において、実施の形態１と同様の構成要素については同一の符号とし、詳細な説明は省略する。実施の形態３に係るサーキュレータファン１の軸流羽根２００は、ボス２０２の外側に係合部２１４，２１５，２１６，２１７を有する。仕切り板４００は、板面４０１にボス２０２の直径と同寸法の穴４０２が形成されている。仕切り板４００の外径は、ハブ２０５の内径よりも小さい寸法の形状となっている。穴４０２にはボス２０２が貫通し、係合部２１４，２１５と係合部２１６，２１７との間に挟まれることで、仕切り板４００が軸流羽根２００に固定される。仕切り板４００は、弾性変形によって反らせた状態で係合部２１４，２１５と係合部２１６，２１７との間に嵌め込むことができるが、他の方法で嵌め込んでもよい。また、ボス２０２が貫通する穴４０２の周囲には、少なくとも一つの穴４０４が形成されている。すなわち、板面４０１には、ボス２０２が貫通する穴４０２以外に少なくとも一つの穴４０４が形成されている。他の構成要素については、実施の形態１と同様である。なお、穴４０４の形状、数及び大きさは特に限定はしないが、仕切り板４００は、軸流羽根２００とともに回転するため、回転バランスを崩さないように配置することが好ましい。Embodiment 3.
FIG. 7 is an enlarged side sectional view of the inside of the hub of the circulator fan according to the third embodiment of the present invention. FIG. 8 is a perspective view of a partition plate that divides the inside of the hub of the circulator fan according to the third embodiment. In FIGS. 7 and 8, the same components as those in the first embodiment are designated by the same reference numerals, and detailed description thereof will be omitted. The axial flow blade 200 of the circulator fan 1 according to the third embodiment has engaging portions 214,215,216,217 on the outside of the boss 202. In the partition plate 400, a hole 402 having the same size as the diameter of the boss 202 is formed on the plate surface 401. The outer diameter of the partition plate 400 is smaller than the inner diameter of the hub 205. The partition plate 400 is fixed to the axial flow blade 200 by the boss 202 penetrating the hole 402 and being sandwiched between the engaging portions 214 and 215 and the engaging portions 216 and 217. The partition plate 400 can be fitted between the engaging portions 214 and 215 and the engaging portions 216 and 217 in a state of being warped by elastic deformation, but it may be fitted by another method. Further, at least one hole 404 is formed around the hole 402 through which the boss 202 penetrates. That is, at least one hole 404 is formed on the plate surface 401 in addition to the hole 402 through which the boss 202 penetrates. Other components are the same as those in the first embodiment. The shape, number, and size of the holes 404 are not particularly limited, but since the partition plate 400 rotates together with the axial flow blade 200, it is preferable to arrange the partition plate 400 so as not to disturb the rotation balance.

ハブ２０５の内部に設置された仕切り板４００が空間５００を空間５０１と空間５０２とに隔てることにより、共鳴が発生する空間は図７に示す空間５０２となる。仕切り板４００を設置した場合には、共鳴が発生する空間の軸流羽根２００の回転軸方向の寸法は、ハブ２０５の前面２０５ａと仕切り板４００との間の寸法Ａと仕切り板４００と電動機フレーム１０３との間の寸法Ｂとの和であるＡ＋Ｂから仕切り板４００と電動機フレーム１０３との間の寸法であるＢに変化する。また、仕切り板４００を設置した場合には、共鳴が発生する空間の体積は、ハブ２０５の前面２０５ａと仕切り板４００との間の空間５０１の体積Ｖ１と仕切り板４００と電動機フレーム１０３との間の空間５０２の体積Ｖ２との和であるＶ１＋Ｖ２から仕切り板４００と電動機フレーム１０３との間の空間５０２の体積であるＶ２に変化する。したがって、仕切り板４００を設置することにより、気柱共鳴及びヘルムホルツ共鳴の周波数が変化する。また、ハブ２０５の内径と仕切り板４００の外周４０３との間には間隙があり、仕切り板４００の板面４０１には穴４０４が形成されているため、空間５０１にもヘルムホルツ共鳴が発生し、穴４０４が存在する板面４０１を含む広範囲で共鳴消音の効果が得られる。 The partition plate 400 installed inside the hub 205 separates the space 500 into the space 501 and the space 502, so that the space where resonance occurs becomes the space 502 shown in FIG. 7. When the partition plate 400 is installed, the dimensions of the axial flow blade 200 in the space where resonance occurs in the rotation axis direction are the dimension A between the front surface 205a of the hub 205 and the partition plate 400, the partition plate 400, and the motor frame. It changes from A + B, which is the sum of the dimension B between the 103 and the partition plate 400, to B, which is the dimension between the partition plate 400 and the motor frame 103. When the partition plate 400 is installed, the volume of the space where resonance occurs is between the volume V1 of the space 501 between the front surface 205a of the hub 205 and the partition plate 400, the partition plate 400, and the motor frame 103. V1 + V2, which is the sum of the volume V2 of the space 502, changes to V2, which is the volume of the space 502 between the partition plate 400 and the motor frame 103. Therefore, by installing the partition plate 400, the frequencies of the air column resonance and the Helmholtz resonance change. Further, since there is a gap between the inner diameter of the hub 205 and the outer circumference 403 of the partition plate 400 and the hole 404 is formed in the plate surface 401 of the partition plate 400, Helmholtz resonance also occurs in the space 501. A resonance muffling effect can be obtained in a wide range including the plate surface 401 in which the hole 404 is present.

実施の形態３に係るサーキュレータファン１は、軸流羽根２００の形状を変更せずに運転騒音の増幅を防止できる。したがって、電動機１００の軸流羽根２００側の面とハブ２０５とで囲まれる空間５００が形成される構造を有するサーキュレータファン１は、共鳴による運転音の増大を容易に防止できる。 The circulator fan 1 according to the third embodiment can prevent the amplification of operating noise without changing the shape of the axial flow blade 200. Therefore, the circulator fan 1 having a structure in which a space 500 surrounded by the surface of the motor 100 on the axial flow blade 200 side and the hub 205 is formed can easily prevent an increase in operating noise due to resonance.

以上の実施の形態に示した構成は、本発明の内容の一例を示すものであり、別の公知の技術と組み合わせることも可能であるし、本発明の要旨を逸脱しない範囲で、構成の一部を省略、変更することも可能である。 The configuration shown in the above-described embodiment shows an example of the content of the present invention, can be combined with another known technique, and is one of the configurations without departing from the gist of the present invention. It is also possible to omit or change the part.

１ サーキュレータファン、２ スタンド、３ 本体フレーム、４ 電気ユニット、５ 電源コード、１００ 電動機、１０１ シャフト、１０２ 先端部、１０３ 電動機フレーム、１０４ 溝、１０５ Ｃリング、１０６ 樹脂ワッシャ、１０７ ねじ部、１０８ 袋ナット、２００ 軸流羽根、２０１ 中央部、２０２ ボス、２０３ ボス穴、２０４ 翼、２０５ ハブ、２０５ａ 前面、２０６ 開口端、２０７ 端面、２０８，２０９ 差込穴、２１０，２１１，２１２，２１３，２１４，２１５，２１６，２１７ 係合部、３００ 駆動伝達板、３０１，４０１ 板面、３０２，４０２，４０４ 穴、３０３，３０４ 端、３０５，３０６ 爪、４００ 仕切り板、４０３ 外周、５００，５０１，５０２，５０３，５０４ 空間。 1 Circulator fan, 2 stand, 3 body frame, 4 electric unit, 5 power cord, 100 motor, 101 shaft, 102 tip, 103 motor frame, 104 groove, 105 C ring, 106 resin washer, 107 screw part, 108 bags Nut, 200 axial flow blade, 201 central part, 202 boss, 203 boss hole, 204 wing, 205 hub, 205a front, 206 open end, 207 end face, 208,209 insertion hole, 210, 211,212,213,214 , 215, 216, 217 Engagement part, 300 drive transmission plate, 301, 401 plate surface, 302, 402, 404 hole, 303, 304 end, 305, 306 claw, 400 partition plate, 403 outer circumference, 500, 501, 502 , 503,504 Space.

Claims (6)

回転軸を中心にシャフトを回転させる電動機の前記シャフトが貫通されるボスと、
前記電動機側が開口し、前記電動機と反対側が閉塞した円筒形状であって、前記ボスと同軸であり前記ボスの周囲を囲うハブと、
前記ハブの内部に設置されて、前記ハブの内部の空間を二つ以上に隔てる前記シャフトの軸方向に対して垂直な仕切り板とを備え、
前記仕切り板と前記ハブとの境界又は前記仕切り板と前記ボスとの境界には、二つ以上に隔てられた前記空間を繋ぐ隙間が形成されていることを特徴とする軸流羽根。 The boss through which the shaft of the motor that rotates the shaft around the rotating shaft penetrates,
A hub having a cylindrical shape with the motor side open and the side opposite to the motor closed, coaxial with the boss, and surrounding the boss.
It is installed inside the hub and includes a partition plate perpendicular to the axial direction of the shaft that separates the space inside the hub into two or more.
An axial flow vane characterized in that a gap connecting two or more spaces is formed at a boundary between the partition plate and the hub or a boundary between the partition plate and the boss. 前記仕切り板は、前記シャフトが貫通される穴が中央に形成されており、
前記シャフトが前記穴を貫通した前記仕切り板は、前記シャフトに設置されたボス突き当て部と前記ボスとの間に挟まれて前記ボスに固定されることを特徴とする請求項１に記載の軸流羽根。 The partition plate has a hole formed in the center through which the shaft is passed.
The first aspect of claim 1, wherein the partition plate through which the shaft penetrates the hole is sandwiched between a boss abutting portion installed on the shaft and the boss and fixed to the boss. Axial flow blade. 前記仕切り板は、前記ボスが貫通する穴が中央に形成されており、
前記ハブは、内面側に突出する係合部が形成されており、
前記仕切り板は、外縁部を前記係合部に引っ掛けて前記ハブに固定されることを特徴とする請求項１に記載の軸流羽根。 The partition plate has a hole formed in the center through which the boss penetrates.
The hub is formed with an engaging portion that projects toward the inner surface side.
The axial flow blade according to claim 1, wherein the partition plate is fixed to the hub by hooking an outer edge portion on the engaging portion. 前記仕切り板は、前記ボスが貫通する穴が中央に形成されており、
前記ボスは、外周側に突出する係合部が形成されており、
前記仕切り板は、前記穴の縁を前記係合部に引っ掛けて前記ボスに固定されることを特徴とする請求項１に記載の軸流羽根。 The partition plate has a hole formed in the center through which the boss penetrates.
The boss is formed with an engaging portion that protrudes to the outer peripheral side.
The axial flow blade according to claim 1, wherein the partition plate is fixed to the boss by hooking the edge of the hole on the engaging portion. 前記仕切り板は、板面に前記ボスが貫通する穴以外に少なくとも一つの穴が形成されていることを特徴とする請求項１から４のいずれか１項に記載の軸流羽根。 The axial flow blade according to any one of claims 1 to 4, wherein the partition plate has at least one hole formed on the plate surface in addition to the hole through which the boss penetrates. 請求項１から５のいずれか１項に記載の軸流羽根と、前記電動機とを有することを特徴とする送風機。 A blower having the axial flow blade according to any one of claims 1 to 5 and the electric motor.
JP2020508715A 2018-03-29 2018-03-29 Axial blades and blowers Active JP6942242B2 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2018/013288 WO2019186910A1 (en) 2018-03-29 2018-03-29 Axial flow blade, and blower

Publications (2)

Publication Number Publication Date
JPWO2019186910A1 JPWO2019186910A1 (en) 2020-12-03
JP6942242B2 true JP6942242B2 (en) 2021-09-29

Family

ID=68059644

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2020508715A Active JP6942242B2 (en) 2018-03-29 2018-03-29 Axial blades and blowers

Country Status (5)

Country Link
EP (1) EP3779207B1 (en)
JP (1) JP6942242B2 (en)
KR (1) KR102405401B1 (en)
CN (1) CN111919034A (en)
WO (1) WO2019186910A1 (en)

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS54126107U (en) * 1978-02-22 1979-09-03
JPS5530963U (en) * 1978-08-21 1980-02-28
JPS5820395U (en) * 1981-08-03 1983-02-08 三菱電機株式会社 impeller in blower
JPH04259696A (en) * 1991-02-14 1992-09-16 Toshiba Corp Fan
JP2911236B2 (en) * 1991-02-21 1999-06-23 松下電器産業株式会社 Blower
JPH0518398A (en) 1991-07-11 1993-01-26 Matsushita Seiko Co Ltd Axial flow blade
JP2004003452A (en) * 2002-04-09 2004-01-08 Daikin Ind Ltd Impeller of fan
JP2006307666A (en) * 2005-04-26 2006-11-09 Nissan Motor Co Ltd Fan device
KR101189447B1 (en) * 2006-08-30 2012-10-09 엘지전자 주식회사 Outer rotor type fan-motor
GB2449688A (en) * 2007-05-31 2008-12-03 Greenwood Air Man Ltd An impeller / fan having radially extending blades and axially extending blades
JP2010025038A (en) * 2008-07-23 2010-02-04 Panasonic Corp Blower
DE102009003056A1 (en) * 2009-05-13 2010-11-18 Robert Bosch Gmbh Adjusting device for a rotary body, as well as rotary body
DE102010028099A1 (en) * 2010-04-22 2011-10-27 Behr Gmbh & Co. Kg Axial
CN103573717B (en) * 2012-07-24 2018-06-12 德昌电机(深圳)有限公司 Fan and its impeller
ITTO20140004U1 (en) * 2014-01-10 2015-07-10 Johnson Electric Asti S R L FAN FOR A COOLING ELECTRIC FAN, PARTICULARLY FOR A HEAT EXCHANGER FOR A MOTOR VEHICLE
JP6277419B2 (en) * 2014-06-26 2018-02-14 パナソニックＩｐマネジメント株式会社 Blower

Also Published As

Publication number Publication date
KR20200123215A (en) 2020-10-28
JPWO2019186910A1 (en) 2020-12-03
CN111919034A (en) 2020-11-10
EP3779207B1 (en) 2023-07-26
KR102405401B1 (en) 2022-06-03
EP3779207A1 (en) 2021-02-17
WO2019186910A1 (en) 2019-10-03
EP3779207A4 (en) 2021-04-07

Similar Documents

Publication Publication Date Title
US7156611B2 (en) Counterrotating axial blower
US9267505B2 (en) Counter-rotating axial flow fan
US9683579B2 (en) Circulator
US9702373B2 (en) Single suction type centrifugal fan
JP5256184B2 (en) Counter-rotating axial fan
JP2007077890A (en) Double reverse rotation type axial flow blower
US8167562B2 (en) Centrifugal fan and blower having the same
WO2016002142A1 (en) Fan attachment structure
EP2597314A2 (en) Axial-flow fan
US20200309155A1 (en) Blower
JP6942242B2 (en) Axial blades and blowers
KR102147730B1 (en) Blowers with BMC motor that increase ventilation volume and minimize vibration noise
US8025546B2 (en) Ducted fan assembly for radio-controlled model
WO2016181821A1 (en) Centrifugal blower
CN107882774B (en) Reversible fan
US9551345B2 (en) Axial flow fan
JP6277419B2 (en) Blower
JP2006211770A (en) Rotating machine and operation method therefor
JP5617906B2 (en) Centrifugal blower
JP2017044133A (en) Centrifugal blower and ventilator
KR102097201B1 (en) Low vibration sirocco fan
JP6919602B2 (en) Electric blower
JP6760376B2 (en) Centrifugal blower
JP4871303B2 (en) Counter-rotating axial fan
JPH08338396A (en) Centrifugal type air blower

Legal Events

Date Code Title Description
A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20200520

A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20200520

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20210224

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20210412

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20210511

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20210625

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20210810

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20210907

R150 Certificate of patent or registration of utility model

Ref document number: 6942242

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250