JPH1182382A - Impeller for blower - Google Patents
Impeller for blowerInfo
- Publication number
- JPH1182382A JPH1182382A JP9240979A JP24097997A JPH1182382A JP H1182382 A JPH1182382 A JP H1182382A JP 9240979 A JP9240979 A JP 9240979A JP 24097997 A JP24097997 A JP 24097997A JP H1182382 A JPH1182382 A JP H1182382A
- Authority
- JP
- Japan
- Prior art keywords
- impeller
- blade
- boss
- shroud
- wing
- 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.)
- Granted
Links
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、空気調和機などに
用いられる低騒音化を図った送風機用羽根車に関するも
のである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an impeller for a blower which is used for an air conditioner or the like and which has reduced noise.
【０００２】[0002]
【従来の技術】従来より空気調和機などに用いられてい
る送風機は、省エネルギのために高性能化が要求される
一方、環境のために低騒音化が要求されている。そし
て、羽根車の形状の改善による性能、騒音の改善方法が
既に提案されており、その一例として、羽根車翼の三次
元化が効果をあげている。例えば、特開平６−３０７３
９０号公報には、上記送風機に関する技術として、ボ
ス、シュラウド及び個々の翼を各別に作成することによ
り、複雑な三次元翼の作成をする方法が開示されてい
る。2. Description of the Related Art A blower conventionally used in an air conditioner or the like is required to have high performance for energy saving, and is required to have low noise for the environment. Methods for improving the performance and noise by improving the shape of the impeller have already been proposed, and as one example, the use of three-dimensional impeller blades has been effective. For example, JP-A-6-3073
Japanese Patent Publication No. 90 discloses a technique for creating a complicated three-dimensional wing by separately creating a boss, a shroud, and individual wings as a technique related to the blower.
【０００３】[0003]
【発明が解決しようとする課題】しかしながら、上記公
報に開示のものでは、複雑な三次元翼の作成は可能であ
るが、翼、ボス及びシュラウドを個別の金型で作成する
ことから、金型個数を多く必要とし、その結果、費用の
増大を招くという問題があった。However, with the one disclosed in the above publication, a complicated three-dimensional wing can be made, but since the wing, boss, and shroud are made by separate dies, the dies are not made. There is a problem that a large number is required, which results in an increase in cost.
【０００４】前記羽根車翼の樹脂成形を考えた場合、樹
脂の厚さは、一定の方が固まる時間も早く、成形性もよ
いが、前記三次元翼の作成方法では、翼形が複雑である
ために、樹脂の厚さにばらつきが生じ、成形時間の増
大、重量の増加が考えられる。また、個々の翼の重量が
大きく、ボス、シュラウドと別々に作成し、組み合わせ
ることによって回転バランスの低下を招くという問題を
生ずることにもなっていた。[0004] When considering the resin molding of the impeller blades, a resin having a constant thickness has a faster setting time and good moldability, but the method of forming the three-dimensional blade has a complicated blade shape. For this reason, the thickness of the resin varies, which may increase the molding time and the weight. In addition, the weight of each wing is large, and the boss and the shroud are separately manufactured and combined with each other, which causes a problem of lowering the rotational balance.
【０００５】羽根車のボス、シュラウド及び個々の翼を
別々に作成し、これらを組合せることによる回転バラン
スの低下を改善するには、薄肉で翼を形成し、重量低減
を図るとともに、回転軸とつながるボスに対して翼を一
体で成形することが効果的であるが、従来例では、翼形
状が三次元的に複雑であるために、薄肉化にとって有効
な中空成形が困難であるばかりでなく、ボスと翼を一体
で成形するためには、分割可動型での成形が必要とな
り、さらに金型数が増加し、ひいては費用の増大を招く
という前述と同様の問題があった。[0005] In order to reduce the rotational balance caused by separately preparing the boss, shroud and individual blades of the impeller, the blades are formed thin, the weight is reduced, and the rotation shaft is reduced. It is effective to form the wings integrally with the boss that connects to the boss.However, in the conventional example, since the wing shape is three-dimensionally complicated, it is only difficult to form a hollow that is effective for thinning. In order to form the boss and the wing in one piece, it is necessary to form the boss and the wing with a split movable mold, which further increases the number of dies, resulting in an increase in cost.
【０００６】本発明の目的は、上記した諸問題を解決す
るため、特に羽根車翼の樹脂成形品を得るのに、金型個
数つまり、費用の増大を防ぎ、成形時間を短縮し、重量
を低減しつつ、羽根車のアンバランスを解消し、羽根車
入口損失の低減、出口速度分布の均一化により、性能を
改善し、シュラウド近傍の剥離を押さえ、乱流騒音を低
減することのできる送風機用羽根車を提供することにあ
る。SUMMARY OF THE INVENTION An object of the present invention is to solve the above-mentioned problems, and in particular, to obtain a resin molded product of an impeller blade, to prevent an increase in the number of dies, that is, to reduce the cost, to shorten the molding time, and to reduce the weight. A blower that can improve the performance by reducing the impeller unbalance, reducing the impeller inlet loss, and making the outlet speed distribution uniform while reducing the separation near the shroud and reducing turbulent noise An object of the present invention is to provide an impeller.
【０００７】[0007]
【課題を解決するための手段】上記目的を達成するため
の本発明による送風機用羽根車は、請求項１ないし６の
各項に記載されたところをもって構成上の特徴とするも
のである。The blower impeller according to the present invention for attaining the above object has the structural features described in each of claims 1 to 6.
【０００８】すなわち、請求項１による送風機用羽根車
は、回転軸に取付けられるボスと、吸込口を有するシュ
ラウドと、ボス及びシュラウド間に配設される複数枚の
翼と、で構成される送風機用羽根車において、前記羽根
車の中心から半径ｒにとった円筒面と、前記翼の圧力面
もしくは負圧面とのなす交線を、前記回転軸に対して傾
斜させると共に、前記交線における前記翼の圧力面もし
くは負圧面と径方向とのなす角度を、前記羽根車の高さ
方向全域にわたり略同一としたことを特徴とするもので
ある。That is, an impeller for a blower according to claim 1 is a blower including a boss attached to a rotating shaft, a shroud having a suction port, and a plurality of blades arranged between the boss and the shroud. In the impeller, an intersection line between a cylindrical surface having a radius r from the center of the impeller and a pressure surface or a suction surface of the blade is inclined with respect to the rotation axis, and the intersection line at the intersection line is inclined. The angle between the pressure surface or the suction surface of the blade and the radial direction is substantially the same over the entire height direction of the impeller.
【０００９】同じく、請求項２による送風機用羽根車
は、前記請求項１において、前記羽根車の中心から半径
ｒにとった円筒面と前記翼の圧力面もしくは負圧面との
なす交線の前記回転軸に対する傾斜角度を、半径ｒの一
次関数としたことを特徴とするものである。[0009] Similarly, in the blower impeller according to claim 2, in the above-described claim 1, the intersection of a cylindrical surface having a radius r from the center of the impeller and a pressure surface or a suction surface of the blade is formed. The tilt angle with respect to the rotation axis is a linear function of the radius r.
【００１０】同じく、請求項３による送風機用羽根車
は、前記請求項１及び２のいずれかにおいて、ボス側も
しくはシュラウド側の前記羽根車回転軸に垂直な断面に
おける翼形状が、シュラウド側もしくはボス側の前記羽
根車回転軸に垂直な断面における翼形状を内包する形状
であり、翼入口における羽根車回転軸を中心とした円筒
面での翼断面の傾斜を小さくし、ボスと翼、あるいはシ
ュラウドと翼を略垂直に接合したことを特徴とするもの
である。According to a third aspect of the present invention, there is provided the impeller for a blower according to any one of the first and second aspects, wherein a wing shape on a boss side or a shroud side in a section perpendicular to the impeller rotation axis is the shroud side or the boss side. The blade has a shape including the blade shape in a cross section perpendicular to the impeller rotation axis on the side, and reduces the inclination of the blade cross section on the cylindrical surface centered on the impeller rotation axis at the blade inlet, thereby reducing the boss and the blade or the shroud. And the wings are joined substantially vertically.
【００１１】同じく、請求項４による送風機用羽根車
は、前記請求項１ないし３のいずれかにおいて、翼内部
を空洞にしたことを特徴とするものである。[0011] Similarly, a blower impeller according to a fourth aspect is the blower impeller according to any one of the first to third aspects, wherein the inside of the blade is hollow.
【００１２】同じく、請求項５による送風機用羽根車
は、前記請求項１ないし４のいずれかにおいて、前記羽
根車におけるボス、シュラウド及び翼がすべて樹脂製で
あることを特徴とするものである。Similarly, a blower impeller according to a fifth aspect is characterized in that, in any one of the first to fourth aspects, the boss, shroud, and blade of the impeller are all made of resin.
【００１３】同じく、請求項６による送風機用羽根車
は、前記請求項５において、前記羽根車は、前記複数の
翼がボス及びシュラウドのいずれか一方と一体成形され
たのち、それと他方と組合せて構成されていることを特
徴とするものである。According to a sixth aspect of the present invention, in the blower impeller according to the fifth aspect, the plurality of blades are formed integrally with one of a boss and a shroud and then combined with the other. It is characterized by comprising.
【００１４】[0014]
【発明の実施の形態】本発明による実施例を図面を参照
しながら説明する。図１〜５は、本発明の第１実施例に
よる送風機用羽根車の説明図である。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment according to the present invention will be described with reference to the drawings. 1 to 5 are explanatory views of an impeller for a blower according to a first embodiment of the present invention.
【００１５】図１は、第１実施例による羽根車の斜視図
で、６は８枚の翼であり、７はボス、８はシュラウドで
ある。FIG. 1 is a perspective view of an impeller according to the first embodiment, in which 6 is eight blades, 7 is a boss, and 8 is a shroud.
【００１６】図２は、送風機の羽根車回転軸を含む側断
面図で、５は第１実施例による羽根車であり、羽根車５
の吸込み部分には吸込みガイド９が挿入されている。羽
根車５はモータ４により駆動される。FIG. 2 is a side sectional view including the impeller rotating shaft of the blower. Reference numeral 5 denotes an impeller according to the first embodiment.
A suction guide 9 is inserted into the suction portion of the suction pipe. The impeller 5 is driven by the motor 4.
【００１７】図３は、図２における羽根車翼のシュラウ
ド側Ａ−Ａ断面、ボス側Ｂ−Ｂ断面でみた羽根車の回転
軸に直交する翼断面である。シュラウド側Ａ−Ａ断面、
ボス側Ｂ−Ｂ断面と、回転中心から任意の半径ｒにとっ
た円筒面とが、互いに交差する位置における翼の圧力面
の接線Ｃ−Ｃ及びＤ−Ｄと径方向とのなす角度βc 及び
βd は、半径ｒの円筒面内で略同一に設定している。FIG. 3 is a cross-sectional view of the impeller impeller blade shown in FIG. 2, which is orthogonal to the rotation axis of the impeller viewed along the AA cross section on the shroud side and the BB cross section on the boss side. AA cross section on the shroud side,
The angle β c formed between the tangent lines CC and DD of the pressure surface of the blade and the radial direction at a position where the boss side BB cross section and the cylindrical surface taken at an arbitrary radius r from the rotation center intersect each other. And β d are set to be substantially the same within a cylindrical surface having a radius r.
【００１８】図４は、図２における羽根車入口付近の半
径ｒの円筒面Ｅ−Ｅ断面でみた翼６の翼断面であり、６
ａ及び６ｂは、それぞれ翼の圧力面及び負圧面を示す。
半径ｒの円筒面における翼のＥ−Ｅ断面は、羽根車回転
軸５１に対して、略一定の傾斜角度αe で設定してい
る。FIG. 4 is a wing cross section of the wing 6 viewed from a section EE of a cylindrical surface having a radius r near the impeller entrance in FIG.
a and 6b show the pressure surface and the suction surface of the blade, respectively.
The EE cross section of the blade on the cylindrical surface with the radius r is set at a substantially constant inclination angle α e with respect to the impeller rotation shaft 51.
【００１９】以上のように構成された送風機を空気調和
機の室内機に搭載した場合の動作を、図５を用いて説明
する。図５において、空気調和機室内機の筐体２に設置
されたモータ４の駆動力によって羽根車５が回転する
と、吸込みガイド９を介して空気が羽根車５に導かれ、
複数の翼６の間を通過することにより静圧と動圧を付加
され、羽根車５から筐体２内部に吐出さる。この空気が
熱交換器１を通過することにより熱交換を行い、パネル
３の吐出口より室内に吐出される。The operation when the blower constructed as described above is mounted on an indoor unit of an air conditioner will be described with reference to FIG. In FIG. 5, when the impeller 5 rotates by the driving force of the motor 4 installed in the housing 2 of the air conditioner indoor unit, air is guided to the impeller 5 via the suction guide 9,
Static pressure and dynamic pressure are applied by passing between the plurality of blades 6, and are discharged from the impeller 5 into the housing 2. This air exchanges heat by passing through the heat exchanger 1 and is discharged into the room from the discharge port of the panel 3.
【００２０】図４に示すように、翼６入口付近では、軸
方向流れと羽根車回転速度の合成ベクトル方向に流れは
傾斜して流入してくる。この角度に、翼６の傾斜角度α
e をあわせることにより、流れが翼６表面に沿って流れ
るため、翼６入口シュラウド８側での剥離が低減され
る。また、剥離が低減されることにより翼６面上の圧力
変動が低減されると共に、入口での羽根車高さ方向の速
度分布が改善される。このような速度分布の改善効果に
より、翼６の入口における羽根車回転軸高さ方向の流れ
が一様となり、翼６出口におけるボス７からシュラウド
８にかけての流れも均一化される。図３に示す翼６の出
口羽根車回転軸高さ方向に流れが均一化されるため、高
さ方向に一様な仕事が可能となる。As shown in FIG. 4, near the inlet of the blade 6, the flow is inclined and flows in the direction of the combined vector of the axial flow and the impeller rotation speed. At this angle, the inclination angle α of the wing 6
By adjusting e , the flow flows along the surface of the blade 6, so that separation at the inlet shroud 8 side of the blade 6 is reduced. Further, by reducing the separation, the pressure fluctuation on the blade 6 surface is reduced, and the velocity distribution in the height direction of the impeller at the inlet is improved. Due to such an effect of improving the velocity distribution, the flow in the height direction of the impeller rotating shaft at the inlet of the blade 6 becomes uniform, and the flow from the boss 7 to the shroud 8 at the outlet of the blade 6 is also made uniform. Since the flow is made uniform in the height direction of the rotary shaft of the exit impeller of the blade 6 shown in FIG. 3, uniform work can be performed in the height direction.
【００２１】本実施例による羽根車を用いた送風機を図
５の様な空調機室内機等に用いる場合は、羽根車出口で
速度分布が均一であるために、熱交換器１への流入速度
が一様となり、熱交換性能の向上が図れる。また、図５
の羽根車５と熱交換器１の間にヒータ１５等を配置する
場合は、ヒータ１５等から生じる騒音が問題となる。本
実施例では、羽根車出口で速度分布が均一であるため、
不均一な場合に対し、最大速度の低減が図られている。
これによりヒータ等から発生する騒音の低減が図れる。
また、翼６出口が傾斜していることに起因して、翼６の
後流がヒータ１５等の高さ方向にぶつかる位相がずれ、
ヒータ等の表面の圧力変動の位相もずれる。騒音は、同
位相の圧力変動では非常に大きくなるが、このように位
相がずれることにより障害物から発生する騒音を低減で
きる。When the fan using the impeller according to the present embodiment is used for an air conditioner indoor unit as shown in FIG. 5, since the speed distribution at the outlet of the impeller is uniform, the inflow speed into the heat exchanger 1 is increased. And the heat exchange performance can be improved. FIG.
When the heater 15 and the like are arranged between the impeller 5 and the heat exchanger 1, noise generated from the heater 15 and the like becomes a problem. In this embodiment, since the velocity distribution is uniform at the impeller outlet,
For non-uniform cases, the maximum speed is reduced.
Thus, noise generated from the heater and the like can be reduced.
Further, due to the inclination of the outlet of the blade 6, the phase in which the wake of the blade 6 hits the height direction of the heater 15 or the like is shifted,
The phase of the pressure fluctuation on the surface of the heater or the like is also shifted. The noise becomes very large with the same phase pressure fluctuation, but the noise generated from the obstacle can be reduced due to the phase shift.
【００２２】本発明の第２実施例は、図３に示す第１実
施例の翼６形状の前縁付近をさらに厚い翼形とし、この
翼６の内部を中空としたものである。翼６を中実とした
場合は、図３中のＡ−Ａ断面及びＢ−Ｂ断面で示される
翼６のもっとも厚い部分は、図２中のボス７やシュラウ
ド８よりも厚くなる。このような場合、羽根車が重くな
り、材料も多量に使用されることとなる。また、樹脂成
形では、肉厚が大きいために、成形に時間がかかるばか
りでなく、肉厚が不均一であるため、樹脂が固まる際に
生じるの収縮にばらつきが出ることによるりアンバラン
スが生じる等の問題がおきる。In the second embodiment of the present invention, the vicinity of the leading edge of the shape of the wing 6 of the first embodiment shown in FIG. 3 is made thicker, and the inside of the wing 6 is hollow. When the wing 6 is solid, the thickest part of the wing 6 shown by the AA section and the BB section in FIG. 3 is thicker than the boss 7 and the shroud 8 in FIG. In such a case, the impeller becomes heavy and a large amount of material is used. In addition, in resin molding, not only takes a long time to mold due to the large thickness, but also because the thickness is non-uniform, there is a variation in shrinkage that occurs when the resin is hardened, resulting in an unbalance due to unbalance. And other problems.
【００２３】そこで、第２実施例においては、図３の翼
６内部を中空とし、ボス７やシュラウド８の厚さと略同
等の厚さで樹脂成形することにより、ボス及びシュラウ
ドを含む羽根車全体の重量の低減、成形時間の短縮、ア
ンバランスの解消等が図れる。Therefore, in the second embodiment, the entire impeller including the boss and the shroud is formed by hollowing the inside of the blade 6 in FIG. 3 and molding the resin with a thickness substantially equal to the thickness of the boss 7 and the shroud 8. Weight, molding time, and imbalance.
【００２４】図６は本発明の第３実施例における送風機
用羽根車の構造を示す斜視図である。この実施例におい
ては、第１もしくは第２実施例の構成上の特徴を活かし
たうえで、翼６の枚数を４枚に低減したものである。一
般に翼枚数が少なくなると、性能は低下し、一定の流
量、圧力を得るためには、回転数の上昇が必要となり、
この場合、図４に示す回転速度を、軸方向速度に対し大
きくとらなければならず、翼枚数大の時と比べ、羽根車
入口での流れは翼に沿って流れにくくなる。これに対応
して、図６の第３実施例による羽根車では、図３中の翼
６の傾斜角度αeを大きくしたものであり、このように
することにより、翼６入口での流れは翼に添う形とな
り、剥離損失、衝突損失が低減され、速度分布が改善さ
れる。そして、翼６の羽根車回転軸高さ方向の流れが一
様となり、翼６全体で見た場合、羽根車５高さ方向に仕
事が均一化される。FIG. 6 is a perspective view showing the structure of an impeller for a blower according to a third embodiment of the present invention. In this embodiment, the number of blades 6 is reduced to four while taking advantage of the structural features of the first or second embodiment. Generally, as the number of blades decreases, the performance decreases, and in order to obtain a constant flow rate and pressure, it is necessary to increase the number of revolutions.
In this case, the rotation speed shown in FIG. 4 must be set to be higher than the axial speed, and the flow at the impeller inlet is less likely to flow along the blades than when the number of blades is large. Correspondingly, in the impeller according to the third embodiment of FIG. 6, the inclination angle α e of the blade 6 in FIG. 3 is increased, and by doing so, the flow at the inlet of the blade 6 is reduced. The shape follows the wing, and separation loss and collision loss are reduced, and the velocity distribution is improved. Then, the flow of the blade 6 in the height direction of the impeller rotating shaft becomes uniform, and when viewed as a whole of the blade 6, the work is made uniform in the height direction of the impeller 5.
【００２５】また、図３の傾斜角度αe を大きくするこ
とにより、図６に示すように翼６の面積が増大すること
となる。翼６面積が大きくなることにより、流れを拘束
する面積が増大し、翼６形状に流れが沿いやすくなる。
この効果により、さらに翼６の間での速度分布が均一化
され、翼枚数を低減することによる性能低下が抑制され
る。また、騒音は翼６入口剥離の抑制により低減すると
ともに、音源である翼６の枚数に騒音が比例すると考え
られるので、翼６枚数の低減により、さらに低減され
る。By increasing the inclination angle α e in FIG. 3, the area of the wing 6 is increased as shown in FIG. As the area of the wing 6 increases, the area for restricting the flow increases, and the flow easily follows the shape of the wing 6.
Due to this effect, the speed distribution between the blades 6 is further uniformed, and a reduction in performance due to a reduction in the number of blades is suppressed. In addition, the noise is reduced by suppressing the separation at the entrance of the blade 6, and the noise is considered to be proportional to the number of the blades 6 as the sound source. Therefore, the noise is further reduced by reducing the number of the blades 6.
【００２６】また、上記実施例では、図２に示す翼６入
口半径rin での図３に示す傾斜角度αe を用いて、各半
径Ｒにおける翼６の傾斜角度αを、α＝αe ×Ｒ／rin
と設定することにより図３に示すようにボス７側から、
シュラウド８側までの翼６の回転軸に直交する断面形状
を略同一形状とすることができる。[0026] In the above embodiment, by using the inclination angle alpha e shown in FIG. 3 of the wings 6 inlet radius rin shown in FIG. 2, the inclination angle alpha of the blade 6 at each radius R, α = α e × R / rin
By setting as shown in FIG. 3, from the boss 7 side,
The cross-sectional shape orthogonal to the rotation axis of the blade 6 up to the shroud 8 side can be made substantially the same.
【００２７】翼６の傾斜角度を半径ｒの関数とし、回転
軸に直交する断面での翼６形状を略同一とすることによ
り、羽根車を製作する場合には、図７に示す翼６、ボス
上面を形成する上金型１１０を、回転軸中心に、回転し
ながら回転軸方向に移動する可動金型とし、翼６の傾斜
に合わせ、略一定角度で回転させながら樹脂と分離する
ことにより、図６中のボス７と翼６、あるいはシュラウ
ド８と翼６を一体に成形することができる。When the impeller is manufactured by making the inclination angle of the blade 6 a function of the radius r and making the shape of the blade 6 in a cross section perpendicular to the rotation axis substantially the same, the blade 6 shown in FIG. The upper mold 110 that forms the upper surface of the boss is a movable mold that moves in the rotation axis direction while rotating about the rotation axis, and is separated from the resin while rotating at a substantially constant angle in accordance with the inclination of the blade 6. 6, the boss 7 and the wing 6 or the shroud 8 and the wing 6 can be integrally formed.
【００２８】ボス７もしくはシュラウド８のいずれか一
方と翼６とを一体成形できることは、羽根車の組み立て
精度の向上と生産性の向上、金型個数の低減が図れる。
また、第２実施例のように、翼６内部を中空とした場合
でも、中空形状は翼６の形状のように羽根車高さ方向に
同一とできるので、図７に示す可動金型１１０のＦ−Ｆ
断面を図８の様にすることにより、翼６を中空に成形
し、その肉厚を略一定とすることが可能となる。これに
より、成形時間の短縮、アンバランスの改善、材料の低
減等が図れる。The ability to integrally mold either the boss 7 or the shroud 8 with the blades 6 can improve the assembly accuracy of the impeller, improve productivity, and reduce the number of dies.
Further, even when the inside of the wing 6 is hollow as in the second embodiment, the hollow shape can be the same in the height direction of the impeller like the shape of the wing 6, so that the movable mold 110 shown in FIG. FF
By making the cross section as shown in FIG. 8, it becomes possible to form the wing 6 to be hollow and make its thickness substantially constant. Thereby, shortening of molding time, improvement of imbalance, reduction of material, etc. can be achieved.
【００２９】翼６及びボス７を一体成形する金型は、図
８に示すように、翼６、ボス７上面、中空部８１を形成
する回転可動式上型１１０とボス下面を形成する下型１
００とからなる。このように一体中空成形されたボス７
及び翼６は、該翼６上面に中空部が露出する構造とな
る。そこで、シュラウド８をこの中空部に合わた突起１
２３、翼６をはめ込む二つの溝１２４をもつように成形
すると、一体成形されたボス７及び翼６と、別の型で作
られたシュラウド８とを接合する際、ボス７の回転中心
と、シュラウド８の回転中心にずれがなく、接合後もア
ンバランスの小さい羽根車を成形することが可能であ
る。As shown in FIG. 8, the mold for integrally molding the wing 6 and the boss 7 is a rotatable upper mold 110 for forming the wing 6, the upper surface of the boss 7 and the hollow portion 81, and a lower mold for forming the lower surface of the boss. 1
00. The boss 7 thus integrally formed into a hollow.
The blade 6 has a structure in which a hollow portion is exposed on the upper surface of the blade 6. Then, the shroud 8 is fitted to the projection 1 fitted to this hollow portion.
23, when formed to have two grooves 124 into which the wings 6 are fitted, when the integrally formed boss 7 and the wings 6 are joined to the shroud 8 made by another mold, There is no shift in the center of rotation of the shroud 8, and it is possible to form an impeller with small unbalance even after joining.
【００３０】なお、シュラウド８を成形する金型は、図
８に示すように、シュラウド上面を作成する上型１２
２、翼６側の突起１２３、溝１２４を形成するための下
型１２１から構成される。As shown in FIG. 8, a mold for molding the shroud 8 is an upper mold 12 for forming an upper surface of the shroud.
2. It comprises a lower mold 121 for forming a projection 123 and a groove 124 on the wing 6 side.
【００３１】また、第３実施例のように、図４に示す傾
斜角度αe を大きくとったものにすると、翼６自身が、
ボス７及びシュラウド８に対して大きく傾斜することに
なり、ボス７あるいはシュラウド８との接合面の機械的
な強度が低下する恐れがある。そこで、図９に示すよう
に図２におけるシュラウド側のＡ−Ａ断面及びボス側の
Ｂ−Ｂ断面のうち、シュラウド側のＡ−Ａ断面形状９２
の翼入口位置を、前記手法によるＢ−Ｂ断面形状９１よ
り大径にし、内包される断面形状９０とすることによ
り、厚さの厚い翼６入口付近のボス側断面９１前縁、シ
ュラウド側断面９２前縁を結ぶ線が、ボス７、シュラウ
ド８に対し略垂直に接することとなり、接合強度を確保
でき、羽根車５の機械的強度を高めることができる。When the inclination angle α e shown in FIG. 4 is made large as in the third embodiment, the wing 6 itself becomes
As a result, the mechanical strength of the joint surface with the boss 7 or the shroud 8 may be reduced. Therefore, as shown in FIG. 9, of the AA section on the shroud side and the BB section on the boss side in FIG.
The wing inlet position is made larger in diameter than the BB cross-sectional shape 91 according to the above-mentioned method, and is included in the cross-sectional shape 90, so that the boss side cross-section 91 front edge near the thicker blade 6 inlet and the shroud side cross-section The line connecting the 92 leading edges comes into contact with the boss 7 and the shroud 8 substantially perpendicularly, so that the joining strength can be secured and the mechanical strength of the impeller 5 can be increased.
【００３２】この場合、同一半径におけるボス側の翼断
面９１の厚さを、シュラウド側断面９２より厚くするこ
とにより、図７、８に示すような金型で、ボス及び翼を
一体に成形することが可能である。In this case, the boss and the wing are integrally formed using a mold as shown in FIGS. 7 and 8 by making the thickness of the boss side wing section 91 of the same radius larger than the shroud-side cross section 92. It is possible.
【００３３】上記成形は、図７に示す回転、可動型以外
の方法でも、図１０に示すように、翼間可動金型７４を
軸方向に移動させた場合でも、翼６の圧力面７３また
は、負圧面７２に翼間可動金型７４が当たらない程度、
径方向に移動させた上で、さらに回転軸方向に移動させ
ることにより可能である。The above-described molding can be performed by a method other than the rotating and movable mold shown in FIG. 7 or by moving the movable mold 74 between blades in the axial direction as shown in FIG. To the extent that the movable mold 74 between blades does not hit the suction surface 72,
This can be achieved by moving in the direction of the rotation axis after moving in the radial direction.
【００３４】図４に示したＥ−Ｅ断面を図１１に示すよ
うに圧力面だけを傾斜１０９した形状、あるいは負圧面
だけを傾斜１０８した形状とすることにより、上記に示
したような回転軸中心に回転しない回転軸方向への可動
で羽根車を作成することも可能である。また、このよう
な場合、翼断面の板厚が大きくなるために、図１１の負
圧面だけを傾斜１０８した形状で示すように、板厚の厚
い部分を削除することにより、重量低減、成形性の向上
が図れる。By forming the cross section EE shown in FIG. 4 into a shape in which only the pressure surface is inclined 109 as shown in FIG. 11 or a shape in which only the suction surface is inclined 108, as shown in FIG. It is also possible to create an impeller by moving in the direction of the rotation axis that does not rotate about the center. In such a case, since the plate thickness of the blade cross section becomes large, as shown in FIG. 11, only the negative pressure surface is shown as a shape inclined 108, the thick plate portion is deleted to reduce weight and formability. Can be improved.
【００３５】図１２は、本発明による羽根車の効果を示
すグラフ図である。従来羽根車、翼枚数１３枚、実施例
の羽根車、翼枚数７である。本発明により、翼枚数低減
による性能低下が抑制されており、特に図４に示す翼入
口での回転速度が、軸方向速度より大きくなる低流量係
数域で、性能の向上が図れている。また、騒音は、羽根
枚数の低減、剥離の抑制等により流量係数全域におい
て、約５dBの低減が図れている。FIG. 12 is a graph showing the effect of the impeller according to the present invention. The number of blades is 13 in the conventional impeller, the number of blades is 13, and the number of blades in the embodiment is 7. According to the present invention, the performance degradation due to the reduction in the number of blades is suppressed, and the performance is improved particularly in a low flow coefficient region where the rotation speed at the blade inlet shown in FIG. 4 is higher than the axial speed. Noise is reduced by about 5 dB over the entire flow coefficient range by reducing the number of blades and suppressing separation.
【００３６】[0036]
【発明の効果】以上説明したように、請求項１に係る発
明の送風機用羽根車によれば、羽根車の中心から半径ｒ
にとった円筒面と翼の圧力面もしくは負圧面とのなす交
線を、回転軸に対して傾斜させると共に、前記交線にお
ける前記翼の圧力面もしくは負圧面と径方向とのなす角
度を、前記羽根車の高さ方向全域にわたり略同一とした
構成であるため、翼入口シュラウド側の剥離を抑制し、
速度分布を均一化することができ、性能の向上、騒音の
低減が図れる。As described above, according to the blower impeller according to the first aspect of the present invention, the radius r from the center of the impeller is obtained.
The line of intersection between the cylindrical surface and the pressure surface or the suction surface of the blade taken at the same angle is inclined with respect to the rotation axis, and the angle between the pressure surface or the suction surface of the blade at the intersection and the radial direction, Because the configuration is substantially the same throughout the height direction of the impeller, the separation of the blade inlet shroud side is suppressed,
The speed distribution can be made uniform, thereby improving performance and reducing noise.
【００３７】また、請求項２に係る発明の送風機用羽根
車によれば、請求項１において、羽根車の中心から半径
ｒにとった円筒面と翼の圧力面もしくは負圧面とのなす
交線の回転軸に対する傾斜角度を、半径ｒの一次関数と
した構成であるため、請求項１に係る発明と同様の性能
の向上、騒音の低減が図れるのに加えてボスもしくはシ
ュラウドと翼との一体成形が可能となる。According to a second aspect of the present invention, there is provided the impeller for a blower according to the first aspect, wherein the intersection line between the cylindrical surface having a radius r from the center of the impeller and the pressure surface or the suction surface of the blade is provided. Since the angle of inclination with respect to the rotation axis is a linear function of the radius r, the same improvement in performance and reduction of noise as in the invention according to claim 1 can be achieved, and also the integration of the boss or shroud with the blades Molding becomes possible.
【００３８】また、請求項３に係る発明の送風機用羽根
車によれば、請求項１または２において、ボス側もしく
はシュラウド側の羽根車回転軸に垂直な断面における翼
形状が、シュラウド側もしくはボス側の羽根車回転軸に
垂直な断面における翼形状を内包する形状とし、翼入口
における羽根車回転軸を中心とした円筒面での翼断面の
傾斜を小さくし、ボスと翼、あるいはシュラウドと翼を
略垂直に接合した構成であるため、前記した効果に加え
て翼が傾斜することによる機械的強度の低下を押えるこ
とができる。According to a third aspect of the present invention, in the blower impeller according to the first or second aspect, the blade shape in a cross section perpendicular to the boss-side or shroud-side impeller rotation axis is the shroud side or the boss. The blade has a shape that includes the blade shape in a cross section perpendicular to the impeller rotation axis on the side, reduces the inclination of the blade cross section on the cylindrical surface around the impeller rotation axis at the blade entrance, and reduces the boss and blade, or the shroud and blade. Are joined substantially perpendicularly, so that in addition to the above-described effects, a decrease in mechanical strength due to the inclination of the blade can be suppressed.
【００３９】さらに、請求項４に係る発明の送風機用羽
根車によれば、請求項１ないし３のいずれかにおいて、
羽根車の内部を空洞にした構成であるため、前記した効
果に加えて羽根車の大巾な重量低減及びアンバランスの
解消をも実現することができる。Further, according to the blower impeller of the invention according to claim 4, according to any one of claims 1 to 3,
Since the inside of the impeller is hollow, in addition to the above-mentioned effects, it is possible to realize a large weight reduction of the impeller and elimination of imbalance.
【図１】第１実施例による８枚翼羽根車の斜視図FIG. 1 is a perspective view of an eight-blade impeller according to a first embodiment.
【図２】図１に示す羽根車を備えた送風機の側断面図FIG. 2 is a side sectional view of a blower provided with the impeller shown in FIG.
【図３】第２の羽根車翼におけるシュラウド側Ａ−Ａ断
面及びボス側Ｂ−Ｂ断面を示す説明図。FIG. 3 is an explanatory diagram showing a cross section of the shroud side AA and a boss side BB of the second impeller blade.
【図４】第２の羽根車翼のＥ−Ｅ断面におけるボス、シ
ュラウド及び翼の相互関係説明図FIG. 4 is an explanatory view showing a relationship between a boss, a shroud, and a blade in an EE section of a second impeller blade;
【図５】図２に示す送風機を倒置して天井に設置した空
気調和機室内機の側断面図FIG. 5 is a side sectional view of the air conditioner indoor unit in which the blower shown in FIG. 2 is inverted and installed on a ceiling;
【図６】第３実施例による４枚翼羽根車の斜視図FIG. 6 is a perspective view of a four-blade impeller according to a third embodiment.
【図７】羽根車成形用金型の１例を示す説明図FIG. 7 is an explanatory view showing an example of an impeller molding die.
【図８】図７に示す羽根車成形用金型のＦ−Ｆ断面でみ
た説明図FIG. 8 is an explanatory view of the impeller molding die shown in FIG.
【図９】第３実施例よる羽根車のシュラウド側Ａ−Ａ断
面及びボス側Ｂ−Ｂ断面を示す説明図FIG. 9 is an explanatory view showing an AA cross section on the shroud side and a BB cross section on the boss side of the impeller according to the third embodiment.
【図１０】羽根車成形用金型の他の例を示す説明図FIG. 10 is an explanatory view showing another example of an impeller molding die.
【図１１】他の実施例による羽根車翼のＥ−Ｅ断面にお
けるボス、シュラウド及び翼の相互関係説明図FIG. 11 is an explanatory view showing a relationship between a boss, a shroud, and a blade in an EE section of an impeller blade according to another embodiment.
【図１２】本発明による羽根車の効果を示すグラフ図FIG. 12 is a graph showing the effect of the impeller according to the present invention.
１…熱交換器 ２…筐体 ３…パネル ４…モータ ５…羽根車 ６…翼 ７…ボス ８…シュラウド ９…吸込みガイド １５…ヒータ ５１…羽根車回転軸 ７２…翼負圧面 ７３…翼圧力面 ７４…翼間可動金型 ９１…翼断面 ９２…翼断面 １００…翼、ボス用下金型 １０８…翼断面 １０９…翼断面 １１０…翼、ボス用上金型 １２１…シュラウド用下金型 １２２…シュラウド用上金型 １２３…翼接合用突起 １２４…翼接合用溝 DESCRIPTION OF SYMBOLS 1 ... Heat exchanger 2 ... Housing 3 ... Panel 4 ... Motor 5 ... Impeller 6 ... Wing 7 ... Boss 8 ... Shroud 9 ... Suction guide 15 ... Heater 51 ... Impeller rotation axis 72 ... Blade negative pressure surface 73 ... Blade pressure Surface 74: Blade movable mold 91: Blade cross section 92: Blade cross section 100: Lower die for wing, boss 108 ... Blade cross section 109: Blade cross section 110: Upper die for wing and boss 121: Lower die for shroud 122 ... Upper mold for shroud 123 ... Protrusion for blade connection 124 ... Groove for blade connection
───────────────────────────────────────────────────── フロントページの続き (72)発明者 長井 誠 静岡県清水市村松390番地 株式会社日立 製作所空調システム事業部内 (72)発明者 佐藤 良次 静岡県清水市村松390番地 株式会社日立 製作所空調システム事業部内 (72)発明者 米山 裕康 静岡県清水市村松390番地 株式会社日立 製作所空調システム事業部内 (72)発明者 畑 良樹 静岡県清水市村松390番地 株式会社日立 製作所空調システム事業部内 ──────────────────────────────────────────────────の Continuing on the front page (72) Inventor Makoto Nagai 390 Muramatsu, Shimizu-shi, Shizuoka Prefecture Inside Air Conditioning Systems Division, Hitachi, Ltd. (72) Inventor Ryoji Sato 390 Muramatsu, Shimizu-shi, Shizuoka Prefecture Air Conditioning System, Hitachi, Ltd. Within the business division (72) Inventor Hiroyasu Yoneyama 390 Muramatsu, Shimizu-shi, Shizuoka Prefecture Inside Air Conditioning System Division, Hitachi, Ltd. (72) Inventor Yoshiki Hata 390 Muramatsu, Shimizu-shi, Shizuoka Prefecture Inside Air Conditioning System Division, Hitachi, Ltd.
Claims (6)
有するシュラウドと、ボス及びシュラウド間に配設され
る複数枚の翼と、で構成される送風機用羽根車におい
て、 前記羽根車の中心から半径ｒにとった円筒面と前記翼の
圧力面もしくは負圧面とのなす交線を、前記回転軸に対
して傾斜させると共に、前記交線における前記翼の圧力
面もしくは負圧面と径方向とのなす角度を、前記羽根車
の高さ方向全域にわたり略同一としたことを特徴とする
送風機用羽根車。1. An impeller for a blower, comprising: a boss attached to a rotating shaft; a shroud having an inlet; and a plurality of blades disposed between the boss and the shroud. A line of intersection between the cylindrical surface having a radius r and the pressure surface or the suction surface of the blade is inclined with respect to the rotation axis, and the pressure surface or the suction surface of the blade at the intersection line and the radial direction. The angle formed by the blade is substantially the same over the entire height direction of the impeller.
筒面と前記翼の圧力面もしくは負圧面とのなす交線の前
記回転軸に対する傾斜角度を、半径ｒの一次関数とした
ことを特徴とする請求項１記載の送風機用羽根車。2. The method according to claim 1, wherein an inclination angle of an intersection line between a cylindrical surface having a radius r from the center of the impeller and a pressure surface or a suction surface of the blade with respect to the rotation axis is a linear function of a radius r. The impeller for a blower according to claim 1, characterized in that:
羽根車回転軸に垂直な断面における翼形状が、前記シュ
ラウド側もしくはボス側の前記羽根車回転軸に垂直な断
面における翼形状を内包する形状であり、翼入口におけ
る羽根車回転軸を中心とした円筒面での翼断面の傾斜を
小さくし、ボスと翼、あるいはシュラウドと翼を略垂直
に接合したことを特徴とする請求項１及び２のいずれか
に記載の送風機用羽根車。3. A blade shape in a cross section perpendicular to the impeller rotation axis on the boss side or the shroud side includes a blade shape in a cross section perpendicular to the impeller rotation axis on the shroud side or the boss side. And a boss and a wing or a shroud and a wing are joined substantially perpendicularly at a wing inlet at a blade surface on a cylindrical surface centered on an impeller rotation axis. An impeller for a blower according to any one of the above.
特徴とする請求項１ないし３のいずれかに記載の送風機
用羽根車。4. The impeller for a blower according to claim 1, wherein the inside of said impeller blade is hollow.
び翼がすべて樹脂製であることを特徴とする請求項１な
いし４のいずれかに記載の送風機用羽根車。5. The impeller for a blower according to claim 1, wherein the boss, the shroud, and the wing of the impeller are all made of resin.
シュラウドのいずれか一方と一体成形されたのち、それ
と他方と組合せて構成されていることを特徴とする請求
項５記載の送風機用羽根車。6. The blower according to claim 5, wherein the impeller is configured such that the plurality of blades are integrally formed with one of a boss and a shroud and then combined with the other. Impeller.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24097997A JP3513367B2 (en) | 1997-09-05 | 1997-09-05 | Impeller for blower |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24097997A JP3513367B2 (en) | 1997-09-05 | 1997-09-05 | Impeller for blower |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH1182382A true JPH1182382A (en) | 1999-03-26 |
| JP3513367B2 JP3513367B2 (en) | 2004-03-31 |
Family
ID=17067519
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP24097997A Expired - Fee Related JP3513367B2 (en) | 1997-09-05 | 1997-09-05 | Impeller for blower |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3513367B2 (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100416777B1 (en) * | 2001-08-01 | 2004-01-31 | 엘지전자 주식회사 | Turbo fan |
| KR100442271B1 (en) * | 2002-01-03 | 2004-07-30 | 엘지전자 주식회사 | turbofan structure |
| US6769876B2 (en) | 2001-09-17 | 2004-08-03 | Nippon Soken, Inc. | Centrifugal ventilator fan |
| JP2012154339A (en) * | 2012-04-06 | 2012-08-16 | Kawamoto Pump Mfg Co Ltd | Method of manufacturing impeller |
| JP2017020409A (en) * | 2015-07-10 | 2017-01-26 | 株式会社日本自動車部品総合研究所 | Centrifugal fan and its manufacturing method |
| CN106895026A (en) * | 2017-04-20 | 2017-06-27 | 河南工学院 | A kind of assembled closed type draught fan impeller |
| WO2020218037A1 (en) * | 2019-04-25 | 2020-10-29 | 株式会社デンソー | Centrifugal fan and blower equipped with said centrifugal fan |
-
1997
- 1997-09-05 JP JP24097997A patent/JP3513367B2/en not_active Expired - Fee Related
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100416777B1 (en) * | 2001-08-01 | 2004-01-31 | 엘지전자 주식회사 | Turbo fan |
| US6769876B2 (en) | 2001-09-17 | 2004-08-03 | Nippon Soken, Inc. | Centrifugal ventilator fan |
| KR100442271B1 (en) * | 2002-01-03 | 2004-07-30 | 엘지전자 주식회사 | turbofan structure |
| JP2012154339A (en) * | 2012-04-06 | 2012-08-16 | Kawamoto Pump Mfg Co Ltd | Method of manufacturing impeller |
| JP2017020409A (en) * | 2015-07-10 | 2017-01-26 | 株式会社日本自動車部品総合研究所 | Centrifugal fan and its manufacturing method |
| CN106895026A (en) * | 2017-04-20 | 2017-06-27 | 河南工学院 | A kind of assembled closed type draught fan impeller |
| WO2020218037A1 (en) * | 2019-04-25 | 2020-10-29 | 株式会社デンソー | Centrifugal fan and blower equipped with said centrifugal fan |
| JP2020180588A (en) * | 2019-04-25 | 2020-11-05 | 株式会社デンソー | Centrifugal fan, and blower including centrifugal fan |
| CN113728165A (en) * | 2019-04-25 | 2021-11-30 | 株式会社电装 | Centrifugal fan and blower with the same |
| US11761456B2 (en) | 2019-04-25 | 2023-09-19 | Denso Corporation | Centrifugal fan and blower equipped with the centrifugal fan |
| CN113728165B (en) * | 2019-04-25 | 2024-03-22 | 株式会社电装 | Centrifugal fan and blower provided with same |
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| Publication number | Publication date |
|---|---|
| JP3513367B2 (en) | 2004-03-31 |
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