JPH0315698A - Impeller of axial blower - Google Patents
Impeller of axial blowerInfo
- Publication number
- JPH0315698A JPH0315698A JP1149035A JP14903589A JPH0315698A JP H0315698 A JPH0315698 A JP H0315698A JP 1149035 A JP1149035 A JP 1149035A JP 14903589 A JP14903589 A JP 14903589A JP H0315698 A JPH0315698 A JP H0315698A
- Authority
- JP
- Japan
- Prior art keywords
- hub
- impeller
- blade
- holes
- blades
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 230000002093 peripheral effect Effects 0.000 claims abstract description 7
- 238000004299 exfoliation Methods 0.000 abstract 2
- 238000000926 separation method Methods 0.000 description 13
- 238000007664 blowing Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 238000009423 ventilation Methods 0.000 description 2
- 244000309466 calf Species 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
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
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
- F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
- F04D29/684—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps by fluid injection
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
産業上の利用分野
本発明は、空気調和機などに用いられる軸流送風機の羽
根車に関するものである。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to an impeller for an axial blower used in an air conditioner or the like.
従来の技術
近年、軸流送風機の羽根車は、セパレート型空気調和機
などの送風機として、業務用から家庭用1で幅広く使用
されてかり、より低騒音化が望1れる傾向にある。BACKGROUND OF THE INVENTION In recent years, the impeller of an axial blower has been widely used as a blower for separate air conditioners, from commercial use to home use, and there is a trend toward lower noise.
以下、図面を参照しながら、上述した従来の軸流送風機
の羽根車について説明する。Hereinafter, the impeller of the conventional axial flow blower mentioned above will be explained with reference to the drawings.
第3図から第7図は従来の軸流送風機の羽根車の構造を
示すものである。1は軸流送風機の羽根車であり、2は
複数の羽根で、3は内部がほぼ空洞の略円柱形のハブで
あり、吸込側の面3aには吸込口4を設けてあり、羽根
2の負圧面側2eのハブ側面3bには複数の孔6が設け
てある。6ぱ羽根2の後縁側2bの外周部を囲む吸込側
がベルマウス状のオリフィスリングである。7は羽根車
1を回転させるモータである。3 to 7 show the structure of the impeller of a conventional axial blower. 1 is an impeller of an axial flow blower, 2 is a plurality of blades, and 3 is a substantially cylindrical hub with an almost hollow interior; a suction port 4 is provided on the suction side surface 3a; A plurality of holes 6 are provided in the hub side surface 3b of the negative pressure side 2e. The suction side surrounding the outer periphery of the trailing edge side 2b of the six blades 2 is a bellmouth-shaped orifice ring. 7 is a motor that rotates the impeller 1.
以上のように構成された軸流送風機の羽根車について以
下その動作を説明する。The operation of the impeller of the axial blower constructed as above will be described below.
1ず、モータ7の回転により、羽根車1が所定の方向に
回転し、空気が羽根車1内に流入し、羽根2の作用によ
って静圧と動圧が付加されて羽根車1外へ吐出され送風
作用を為す。1. As the motor 7 rotates, the impeller 1 rotates in a predetermined direction, air flows into the impeller 1, static pressure and dynamic pressure are added to it by the action of the blades 2, and the air is discharged outside the impeller 1. It acts as a blower.
ここで、軸流送風機の羽根車1の翼間全体及び羽根2近
傍の流れは流体に対して遠心力が働くので、チップ側2
Cに片寄って流れハブ側2dに比べチップ側2Cでの流
量が大きくなる傾向がある。Here, since centrifugal force acts on the fluid in the flow between the entire blades of the impeller 1 of the axial blower and in the vicinity of the blades 2, the tip side 2
There is a tendency for the flow rate to be biased toward the tip side 2C and to be larger on the tip side 2C than on the hub side 2d.
したがって、第6図a,bで示す羽根前縁2a’での周
速度Uと、流入気流の絶対速度c1から式β’−tan
””’C1/uで求められる気流流入角β1′と1
ほぼ一致させる羽根人口角β1 は、羽根車1の回転数
と入口半径rから周速Uが、流量から流入気流の絶対速
度C1 が設定されるので、入口半径rによって第6図
で示すようにハブ側2dでは大きくチップ側2Cでは小
さく設定する。Therefore, from the circumferential velocity U at the leading edge 2a' of the blade shown in FIGS. 6a and 6b and the absolute velocity c1 of the inflow air, the formula
The blade population angle β1, which is made to almost match the airflow inflow angle β1' obtained by C1/u, is determined by determining the circumferential speed U from the rotation speed of the impeller 1 and the inlet radius r, and the absolute speed C1 of the inflow airflow from the flow rate. Therefore, the inlet radius r is set to be large on the hub side 2d and small on the tip side 2C, as shown in FIG.
しかし、第4図で示すように羽根車1には空気が前縁側
2aからだけでなく、チップ側2Cからも吸込1れるの
で、ハブ側2dではさらに流量が減少する。そのため、
第7図で示すようにハブ側2dでの気流流入角β1′に
比べ羽根人口角β,が大きくなりすぎ、羽根2の負圧面
側2eで流れの剥離が生じ、この剥離により流れが乱れ
、送風騒音が増加するので、内部がほぼ空洞の略円柱形
のハブ3の吸込側の面3aに吸込口4を設け、羽根2の
負圧面側2eのハブ側面3bに複数の孔6を設けること
により、吸込口4から空気がハプ3の内部に吸込1れ、
側面bの複数の孔5から羽根2のハプ側2dの負圧面側
2eに吹き出し負圧面側2eを流れることで、第2図で
示すように羽根車1に前縁側2aのみならずチップ側2
Cがら空気が吸込筐れることでハブ側2dの流量が大幅
に減少し気流流入角β1′に比べ羽根人口角β1が大き
くなシすぎ負圧面側2eで流れが剥離するのを防ぐ。However, as shown in FIG. 4, air is drawn into the impeller 1 not only from the leading edge side 2a but also from the tip side 2C, so the flow rate is further reduced on the hub side 2d. Therefore,
As shown in FIG. 7, the blade population angle β becomes too large compared to the airflow inflow angle β1' on the hub side 2d, and separation of the flow occurs on the suction side 2e of the blade 2, and this separation causes turbulence of the flow. Since the air blowing noise increases, a suction port 4 is provided on the suction side surface 3a of the substantially cylindrical hub 3 having a substantially hollow interior, and a plurality of holes 6 are provided on the hub side surface 3b on the negative pressure surface side 2e of the blade 2. As a result, air is sucked into the inside of the haptic 3 from the suction port 4,
Air is blown from the plurality of holes 5 on the side surface b to the suction side 2e of the hap side 2d of the blade 2, and flows through the suction side 2e, so that the impeller 1 not only has the leading edge side 2a but also the tip side 2, as shown in FIG.
Since the air is sucked into the housing, the flow rate on the hub side 2d is significantly reduced, and the flow is prevented from separating on the negative pressure side 2e since the blade population angle β1 is larger than the airflow inflow angle β1'.
発明が解決しようとする課題
しかしながら、上記のような構成では、ハプ3の内部の
空洞と羽根2の負圧面側2eとの間の圧力差は、空気が
ハブ3内部から複数の孔6を通して羽根2の負圧面側2
eに吹き出すほど大きくないので、第7図で示すように
吸込口4からハプ3の内部の空洞に吸込1れた空気は複
数の孔6から吹出すことなく、ハプ3の内部を通って羽
根車1外に吐出してし1うという課題を有していた。Problems to be Solved by the Invention However, in the above configuration, the pressure difference between the internal cavity of the hub 3 and the negative pressure side 2e of the blade 2 is caused by air flowing from the inside of the hub 3 through the plurality of holes 6 to the blade. 2 negative pressure side 2
Since the air is not so large as to be blown out into the haptic 3, as shown in FIG. The problem was that it was discharged outside the vehicle.
本発明は上記課題に鑑み、略円柱形のハブの吸込側の面
に設けた吸込口からハブ内部の空洞に吸込渣れた空気を
、前記羽根負圧面側のハブ側面に設けた複数の孔から強
制的にハブ側の羽根負圧面側に吹き出し、吹き出した気
流が負圧面側を流れることにより、流れの剥離を防ぎ、
剥離による流れの乱れを抑える軸流送風機の羽根車を提
供するものである。In view of the above-mentioned problems, the present invention has provided air sucked into a cavity inside the hub from a suction port provided on the suction side surface of a substantially cylindrical hub through a plurality of holes provided on the hub side surface on the negative pressure surface side of the blade. The air is forcibly blown out to the negative pressure side of the blade on the hub side, and the blown airflow flows on the negative pressure side, preventing flow separation.
The present invention provides an impeller for an axial blower that suppresses flow disturbances caused by separation.
課題を解決するための手段
この目的を達或するために本発明の軸流送風機の羽根車
は複数の羽根と、前記複数の羽根を固定する内部がほぼ
空洞の略円柱形のハブとで構成され、前記略円柱形のハ
ブの吸込側の面に吸込口を設け、前記羽根負圧側のハブ
側面に複数の孔を設け、前記複数の孔があるハブ側面の
内周側の壁面に補助翼を設けている。Means for Solving the Problems To achieve this object, the impeller of the axial blower of the present invention is composed of a plurality of blades and a substantially cylindrical hub having a substantially hollow interior to which the plurality of blades are fixed. A suction port is provided on the suction side surface of the substantially cylindrical hub, a plurality of holes are provided on the hub side surface on the negative pressure side of the blade, and an aileron is provided on the inner peripheral side wall surface of the hub side surface where the plurality of holes are located. has been established.
作 用
との構戊によって、略円柱形のハブの吸込側の面に設け
た吸込口からハブ内部の空洞に空気を吸込み、吸込んだ
空気を前記複数の孔があるハブ側面の内周側の壁面に設
けた補助翼による送風作用で、前記ハブ側面に設けた複
数の孔から強制的にハブ側の羽根負圧面側に吹き出し、
吹き出した気流がハブ側の羽根負圧面側を流れることに
より、流れの剥離を防ぎ、剥離による流れの乱れを抑え
る。Depending on the structure, air is sucked into the cavity inside the hub from the suction port provided on the suction side surface of the substantially cylindrical hub, and the sucked air is sucked into the inner peripheral side of the hub side surface where the plurality of holes are located. Due to the blowing action of the ailerons provided on the wall surface, the air is forcibly blown out from the plurality of holes provided on the side surface of the hub toward the negative pressure side of the blade on the hub side,
The blown airflow flows on the negative pressure side of the blade on the hub side, preventing flow separation and suppressing flow turbulence due to separation.
実施例
以下、本発明の一実施例について図面を参照しながら説
明する。尚、従来例と同一部分については重複を避ける
ため、同一の番号を付けて説明を省略する。EXAMPLE Hereinafter, an example of the present invention will be described with reference to the drawings. Incidentally, in order to avoid duplication, the same parts as in the conventional example are given the same numbers and the description thereof will be omitted.
第1図,第2図は本発明の一実施例にかける軸流送風機
の羽根車の構造を示すものであるっ8は軸流送風機の羽
根車で、9は内部がほぼ空洞の略円柱形のハブ3の複数
の孔6がある羽根2の負圧面側2eのハブ側面3bの内
周側の壁面3Cに、多翼送風機の翼列となるように配設
した補助翼である。Figures 1 and 2 show the structure of an impeller for an axial blower according to an embodiment of the present invention. 8 is the impeller of the axial blower, and 9 is a substantially cylindrical impeller with an almost hollow interior. These auxiliary blades are arranged on the inner wall surface 3C of the hub side surface 3b on the suction surface side 2e of the blade 2 where the plurality of holes 6 of the hub 3 are located so as to form a blade row of a multi-blade blower.
以上のように構成された軸流送風機の羽根車について以
下その動作を説明する。The operation of the impeller of the axial blower constructed as above will be described below.
羽根車8が、モータ了の回転により所定の方向に回転し
、空気が羽根車1内に流入し、羽根2の作用によって静
圧と動圧が付加されて羽根車8外へ吐出され送風作用を
為す。The impeller 8 rotates in a predetermined direction due to the rotation of the motor, air flows into the impeller 1, static pressure and dynamic pressure are added to it by the action of the blades 2, and the air is discharged outside the impeller 8, creating a blowing effect. to do.
ここで、内部曳がほぼ空洞の略円柱形のハブ3の複数の
孔5がある羽根2の負圧面側2eのハブ側面3bの内周
側の壁面3Cに補助m9を多翼送風機の翼列となるよう
に配設することにより、第2図で示すように吸込口8が
ら空気が八ブ3の内部に吸込1れ、吸込んだ空気を複数
の孔6があるハブ側面3bの内側の壁面3Cに設けた補
助翼9による遠心送風作用で、ハブ側面3bに設けた複
数の孔5から強制的に羽根2のハブ側2dの負圧面側2
eに吹き出し、吹き出した気流が負圧面側2eを流れる
ことで、ハブ側2dの流量減少に伴うハブ側2dの負圧
面側2eでの流れの剥離を防ぐ。Here, an auxiliary m9 is attached to the inner peripheral side wall surface 3C of the hub side surface 3b of the suction surface side 2e of the blade 2 where the plurality of holes 5 of the substantially cylindrical hub 3 having a substantially hollow internal space is provided. As shown in FIG. Due to the centrifugal air blowing action by the ailerons 9 provided at 3C, the negative pressure side 2 of the hub side 2d of the blade 2 is forced through the plurality of holes 5 provided on the hub side surface 3b.
Since the airflow is blown out on the negative pressure side 2e and flows on the negative pressure side 2e, separation of the flow on the negative pressure side 2e of the hub side 2d due to a decrease in the flow rate on the hub side 2d is prevented.
以上のように本実施例によれば、内部がほぼ空洞の略円
柱形のハプ3の複数の孔5がある羽根2の負圧面側2e
のハブ側面3bの内周側の壁面3Cに補助翼9を多翼送
風機の翼列となるように配設することによb1吸込口8
からハプ3の内部に吸込壕れた空気が、ハブ側面′3b
の内周側の壁和Cに設けた補助翼9の遠心送風作用によ
り、複数の孔6から強制的に羽根2のハブ側2dの負圧
面側2eに吹き出すことで、ハブ側2dの流量減少に伴
うハブ側2dの負圧面側2eでの流れの剥離を防ぐのに
必要な気流が負圧面側2eを流れ、流れの剥離を防ぎ、
剥離による流れの乱れを乱え、送風騒音の増加を防ぐこ
とができる。As described above, according to the present embodiment, the suction surface side 2e of the blade 2 has a plurality of holes 5 of the substantially cylindrical hub 3 having a substantially hollow interior.
By arranging the ailerons 9 on the inner wall surface 3C of the hub side surface 3b so as to form a row of blades of a multi-blade blower, the b1 suction port 8
The air sucked into the inside of the hub 3 from the hub side '3b
Due to the centrifugal blowing action of the ailerons 9 provided on the wall C on the inner circumferential side of the blades 2, air is forcibly blown out from the plurality of holes 6 to the negative pressure side 2e of the hub side 2d of the blade 2, thereby reducing the flow rate on the hub side 2d. The airflow necessary to prevent flow separation on the negative pressure surface side 2e of the hub side 2d due to this flow flows on the negative pressure surface side 2e, preventing flow separation,
It can disrupt the flow turbulence caused by separation and prevent an increase in ventilation noise.
発明の効果
以上のように本発明の軸流送風機の羽根車は複数の羽根
と、前記複数の羽根を固定する内部がほぼ空洞の略円柱
形のハブとで構成され、前記略円柱形のハブの吸込側の
面に吸込口を設け、前記羽根負圧面側のハブ側面に複数
の孔を設け、前記複数の孔があるハブ側面の内周側の壁
面に補助翼を設けることにより、前記吸込口から吸込1
れた空気が、前記複数の孔から強制的に羽根のハブ側の
負圧面側に吹き出し、羽根のハブ側の負圧面側での流れ
の剥離を防ぐのに必要な気流が負圧面側を流れ、流れの
剥離を防ぎ、剥離による流れの乱れを抑え、送風騒音の
増加を防ぐことができる。Effects of the Invention As described above, the impeller of the axial blower of the present invention is composed of a plurality of blades and a substantially cylindrical hub having a substantially hollow interior to which the plurality of blades are fixed, and the substantially cylindrical hub has a substantially hollow interior. A suction port is provided on the suction side surface of the blade, a plurality of holes are provided on the hub side surface on the side of the suction side of the blade, and an aileron is provided on the inner peripheral side wall surface of the hub side surface where the plurality of holes are located. Inhalation from mouth 1
The air is forcibly blown out from the plurality of holes to the negative pressure side of the hub side of the blade, and the airflow necessary to prevent flow separation on the negative pressure side of the hub side of the blade flows on the negative pressure side of the blade. , it is possible to prevent flow separation, suppress flow turbulence caused by separation, and prevent an increase in ventilation noise.
第1図は本発明の一実施例にかける軸流送風機の羽根車
の斜視図、第2図は本発明の一実施例に訃ける軸流送風
機の羽根車の要部子午断面図、第3図は従来の軸流送風
機の羽根車の斜視図、第4図は従来の軸流送風機の羽根
車の子牛断面図、第6図aは従来の羽根車の平面図、第
6図bは第5図aのA−A/線の断面図、第6図は従来
の羽根車の羽根入口角β1 と入口半径rの関係を示す
図、第7図は第6図aのB−B’線の断面図である。
8・・・・・・軸胤送風機の羽根車、2・・・・・・羽
根、2e・・・・・・負圧面側、3・・・・・・ハブ、
3a・・・・・・吸込側の面、3b・・・・・・ハブ側
面,3a・・・・・・内周側の壁面、4・・・・・・吸
込口、5・・・・・・複数の孔、9・・・・・・補助翼
。FIG. 1 is a perspective view of an impeller of an axial blower according to an embodiment of the present invention, FIG. 2 is a meridional cross-sectional view of essential parts of an impeller of an axial blower according to an embodiment of the present invention, and FIG. The figure is a perspective view of the impeller of a conventional axial flow blower, FIG. 4 is a sectional view of the calf of the impeller of a conventional axial blower, FIG. FIG. 6 is a diagram showing the relationship between the blade inlet angle β1 and the inlet radius r of a conventional impeller, and FIG. 7 is a sectional view taken along line A-A in FIG. 6a. It is a sectional view of a line. 8... Impeller of shaft fan, 2... Vane, 2e... Negative pressure side, 3... Hub,
3a...Suction side surface, 3b...Hub side surface, 3a...Inner peripheral side wall surface, 4...Suction port, 5... ...Multiple holes, 9...Aileron.
Claims (1)
洞の略円柱形のハブとで構成され、前記略円柱形のハブ
の吸込側の面に吸込口を設け、前記羽根負圧面側のハブ
側面に複数の孔を設け、前記複数の孔があるハブ側面の
内周側の壁面に補助翼を設けた軸流送風機の羽根車。It is composed of a plurality of blades and a substantially hollow cylindrical hub that fixes the plurality of blades, and a suction port is provided on the suction side surface of the substantially cylindrical hub, and An impeller for an axial blower, in which a plurality of holes are provided on a side surface of a hub, and ailerons are provided on a wall surface on the inner peripheral side of the side surface of the hub where the plurality of holes are located.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP1149035A JPH0315698A (en) | 1989-06-12 | 1989-06-12 | Impeller of axial blower |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP1149035A JPH0315698A (en) | 1989-06-12 | 1989-06-12 | Impeller of axial blower |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH0315698A true JPH0315698A (en) | 1991-01-24 |
Family
ID=15466238
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP1149035A Pending JPH0315698A (en) | 1989-06-12 | 1989-06-12 | Impeller of axial blower |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0315698A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0592498U (en) * | 1992-05-25 | 1993-12-17 | 自動車電機工業株式会社 | Radiator cooling fan |
JP2003083293A (en) * | 2001-09-07 | 2003-03-19 | Denso Corp | Blower |
-
1989
- 1989-06-12 JP JP1149035A patent/JPH0315698A/en active Pending
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0592498U (en) * | 1992-05-25 | 1993-12-17 | 自動車電機工業株式会社 | Radiator cooling fan |
JP2003083293A (en) * | 2001-09-07 | 2003-03-19 | Denso Corp | Blower |
JP4644994B2 (en) * | 2001-09-07 | 2011-03-09 | 株式会社デンソー | Blower |
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