JPH03130598A - Impeller for fluid machine - Google Patents
Impeller for fluid machineInfo
- Publication number
- JPH03130598A JPH03130598A JP26958889A JP26958889A JPH03130598A JP H03130598 A JPH03130598 A JP H03130598A JP 26958889 A JP26958889 A JP 26958889A JP 26958889 A JP26958889 A JP 26958889A JP H03130598 A JPH03130598 A JP H03130598A
- Authority
- JP
- Japan
- Prior art keywords
- boss
- blades
- impeller
- blade
- main plate
- 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
- 239000012530 fluid Substances 0.000 title claims abstract description 35
- 230000007423 decrease Effects 0.000 claims description 9
- 230000002093 peripheral effect Effects 0.000 abstract description 6
- 238000005266 casting Methods 0.000 abstract description 4
- 210000005252 bulbus oculi Anatomy 0.000 description 7
- 210000003128 head Anatomy 0.000 description 5
- 230000000694 effects Effects 0.000 description 2
- 238000000465 moulding Methods 0.000 description 2
- 239000011347 resin Substances 0.000 description 2
- 229920005989 resin Polymers 0.000 description 2
- 241000542420 Sphyrna tudes Species 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
Landscapes
- 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）
この発明はポンプやコンプレッサのような流体機械にお
いて利用されるインペラに関する。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to an impeller used in fluid machines such as pumps and compressors.
（従来技術）
一般に、この種のインペラは中心部にボスを有する主盤
と、この主盤の少なくとも一方の側面から前記ボスの軸
方向に突出する円周方向等間隔に配置された複数の羽根
とを有し、これらの羽根は隣り合う各羽根との間に前記
ボスのまわりから前記主盤の外周部に至る流体通路を形
成して構成されている。このような流体通路は従来ボス
側すなわち入口側から主盤の外周側すなわち出口側に至
り徐々に幅が広くなるように構成されている。(Prior Art) Generally, this type of impeller includes a main plate having a boss in the center, and a plurality of blades arranged at equal intervals in the circumferential direction and protruding from at least one side of the main plate in the axial direction of the boss. These blades are configured such that a fluid passage is formed between each adjacent blade from around the boss to an outer peripheral portion of the main plate. Conventionally, such a fluid passage is configured so that its width gradually increases from the boss side, that is, the inlet side, to the outer peripheral side of the main panel, that is, the outlet side.
本出願人は特許第１０３８８１５号（アメリカ合衆国特
許第４２５３７９８号） （特公昭第５５−９５６０号
）において、従来とは異なり、流体通路を入口側から出
口側に至り徐々に幅が狭くなるように構成したインペラ
を提案しており、このインペラを利用したポンプは従来
に比してはるかに優れた揚程及び効率が得られることが
立証されている。In Patent No. 1038815 (United States Patent No. 4253798) (Japanese Patent Publication No. 55-9560), the present applicant has constructed a fluid passage whose width gradually becomes narrower from the inlet side to the outlet side, unlike the conventional method. It has been proven that pumps using this impeller can achieve far superior head and efficiency compared to conventional impellers.
また本出願人は上記特許の構成を基本構成として特願昭
用６１−０５３３６９号（特開昭第６２−２１０２９７
号）において、羽根が一定厚さ（インペラの円周方向の
厚さで、以下厚さという場合は特に明記しない限り円周
方向の厚さをいう）を有し、かつ後面と前面とが円弧状
をなす、重量バランスに優れかつ製造が簡単なインペラ
を提供している。The present applicant has also filed Japanese Patent Application No. 61-053369 (Japanese Unexamined Patent Publication No. 62-210297) based on the basic structure of the above patent.
), the blades have a constant thickness (thickness in the circumferential direction of the impeller; hereinafter, the term "thickness" refers to the thickness in the circumferential direction unless otherwise specified), and the rear and front surfaces are circular. We offer arc-shaped impellers that have excellent weight balance and are easy to manufacture.
（発明が解決しようとする課題）
しかしながら、上記特願昭用６１−０５３３６９号のよ
うに羽根を一定厚さとした構成では、例えば羽根を金属
板により形成する場合のように、羽根の厚さが比較的薄
い場合には問題はないが、例えばインペラを主盤と羽根
とを含み鋳造や樹脂成形により一体で形成するような場
合には羽根にはある程度以上の厚さが必要となる。この
ため第６図に示すように羽根Ａ−ＡのボスＢ側の部分す
なわち流体通路Ｃ−Ｃの入口部り側の部分Ａ１〜Ａ１に
よってボスＢ側の目玉部Ｅから入口部りに流入する流体
の流れが妨げられ、ポンプの揚程、効率に悪影響をもた
らすため、より改良されたインペラ構造が希求されてい
た。(Problem to be Solved by the Invention) However, in the structure in which the blades have a constant thickness as in the above-mentioned Japanese Patent Application No. 61-053369, the thickness of the blade is There is no problem if the impeller is relatively thin, but if the impeller includes the main plate and the blades and is integrally formed by casting or resin molding, the blades need to be thicker than a certain level. Therefore, as shown in FIG. 6, the flow from the center point E on the boss B side to the inlet portion is caused by the portions A1 to A1 of the vane A-A on the boss B side, that is, the portions A1 to A1 on the inlet side of the fluid passage C-C. Since the flow of fluid is obstructed, which has a negative effect on the head and efficiency of the pump, an improved impeller structure has been desired.
（課題を解決するための手段）
上記従来技術の課題を解決するため本発明の流体機械用
インペラは中心部にボスを有する主盤と、この主盤の少
なくとも一方の側面から前記ボスの軸方向に突出する円
周方向等間隔に配置された複数の羽根とを有し、これら
の羽根は隣り合う各羽根との間に前記ボスのまわりから
前記主盤の外周部に至る流体通路を形成し、かつこれら
の流体通路はその断面積が前記ボスのまわりから前記主
盤の外周に向って徐々に小さくなるように構成され、前
記主盤の回転により前記ボスのまわりの流体を前記流体
通路を経て前記主盤の外周方向に導くようにした流体機
械用インペラであって、前記羽根を前記ボスに近接する
部位を除きその全長に亘りほば均一の厚さを有して形成
し、その前記ボスに近接する部位の断面積を前記ボス側
に向けて徐々に小さくなるように構成しである。(Means for Solving the Problems) In order to solve the problems of the prior art described above, an impeller for a fluid machine according to the present invention includes a main plate having a boss in the center, and an axial direction of the boss from at least one side of the main plate. and a plurality of blades arranged at equal intervals in the circumferential direction protruding from the main plate, and these blades form a fluid passage between the adjacent blades from around the boss to the outer periphery of the main plate. , and these fluid passages are configured such that their cross-sectional area gradually decreases from around the boss toward the outer periphery of the main plate, and the rotation of the main plate causes the fluid around the boss to flow through the fluid passage. The impeller for a fluid machine is configured such that the blades are formed to have a substantially uniform thickness over the entire length except for a portion close to the boss, and the blades are formed to have a substantially uniform thickness over the entire length thereof, The structure is such that the cross-sectional area of a portion close to the boss gradually becomes smaller toward the boss.
（作用）
本発明の流体機械用インペラは各羽根の間に形成される
流体通路はその断面積がボスのまわりから主盤の外周に
向って徐々に小さくなっており、また羽根はボスに近接
する部位を除きその全長に亘りほぼ均一の厚さを有して
形成しであるので、上記特願昭用６１−０５３３６９号
におけると同様に、重量バランスに優れ、かつ揚程及び
効率に優れたポンプを構成できる一方、各羽根のボスに
近接する部位の断面積がボス側に向けて徐々に小さくな
るように構成しであるので、流体はボス側から各羽根の
間の入口部に流入するに際し羽根のボス側の端部により
流れが妨げられることなく円滑に流入できる。(Function) In the impeller for fluid machinery of the present invention, the cross-sectional area of the fluid passage formed between each blade gradually decreases from around the boss toward the outer periphery of the main plate, and the blades are close to the boss. Since the thickness of the pump is substantially uniform over its entire length except for the parts where it is exposed, the pump has excellent weight balance, and has excellent head and efficiency, as in the above-mentioned Japanese Patent Application No. 61-053369. On the other hand, since the cross-sectional area of each blade near the boss gradually decreases toward the boss, when fluid flows from the boss side to the inlet between each blade, The end of the blade on the boss side allows the flow to flow smoothly without being obstructed.
（実施例） 次に本発明の実施例を添附の図面を参照して説明する。(Example) Next, embodiments of the present invention will be described with reference to the accompanying drawings.
まず本発明の第１実施例を第１図〜第３図を参照して説
明すると、第１図及び第２図において、インペラ１は中
央部にボス２を有する円板状の主盤３と、この主盤３の
一方の側面からボス２の軸方向に一定＾さで突出する複
数の羽根４〜４を備えている。これらの羽根４〜４は円
周方向等間隔に配置されており、ボス２と羽根４〜４は
鋳造により主盤３と一体に成形されている。また各羽根
４の一端はボス２に対し半径方向に隔てられてボス２と
の間に目玉部５を形成しており、また他端は主１２の周
縁部に至っている。各羽根４はほぼ円弧状をなしており
、相互間に流体通路６を各々形成している。First, a first embodiment of the present invention will be described with reference to FIGS. 1 to 3. In FIGS. 1 and 2, an impeller 1 has a disk-shaped main plate 3 having a boss 2 in the center. , a plurality of blades 4 are provided which protrude from one side of the main plate 3 in the axial direction of the boss 2 at a constant distance. These blades 4 to 4 are arranged at equal intervals in the circumferential direction, and the boss 2 and the blades 4 to 4 are integrally formed with the main plate 3 by casting. Further, one end of each blade 4 is radially separated from the boss 2 to form an eyepiece 5 between the blade 4 and the boss 2, and the other end reaches the peripheral edge of the main body 12. Each vane 4 is substantially arc-shaped and defines a fluid passage 6 therebetween.
ここで、流体通路６の幅はボス２側の入口部７から主盤
３の周縁部側の出口部８に至り徐々に小さくなるように
設定されており、また各羽根４はその全長に至り同一厚
さを有しているが、ボス２側の端部９のみはボス２側に
向かうにつれ厚さが小さくなるように形成されている。Here, the width of the fluid passage 6 is set so that it gradually decreases from the inlet part 7 on the boss 2 side to the outlet part 8 on the peripheral side of the main panel 3, and each blade 4 has a width that gradually decreases from the inlet part 7 on the boss 2 side to the outlet part 8 on the peripheral side of the main panel 3. Although they have the same thickness, only the end 9 on the boss 2 side is formed so that the thickness decreases toward the boss 2 side.
また第２図に示すようにボス２内にはモータ等の回転駆
動軸１０の端部が嵌込まれ、ナツト１１により締付は固
定されている。なお１２は回り止め用のキーである。Further, as shown in FIG. 2, an end portion of a rotary drive shaft 10 of a motor or the like is fitted into the boss 2, and is tightened and fixed by a nut 11. Note that 12 is a key for preventing rotation.
以下上記のような羽根４〜４の具体的な形状及び配置を
第３図を参照して詳しく説明する。なお同図にはインペ
ラ１が説明のため簡略化して示してあり、また説明のた
め羽根４〜４には４Ａ、４Ｂ、４Ｃ・・・がそれぞれ付
番しである。The specific shape and arrangement of the blades 4 to 4 as described above will be explained in detail below with reference to FIG. 3. The impeller 1 is shown in a simplified manner for the sake of explanation, and the blades 4 to 4 are numbered 4A, 4B, 4C, . . . , respectively, for the sake of explanation.
図中羽根４Ａのインペラ１の回転方向（矢印で示す）に
関し前面４Ａ１及び後面４Ａ２は同一の中心Ｐ１を中心
としてそれぞれ半径Ｒ１，Ｒ２の円弧状に形成されてい
る。同様に羽根４Ｂの前面４８１及び後面４Ｂ２は中心
Ｐ２を中心する上記と同様な半径Ｒ１，Ｒ２の円弧状に
形成され、羽根４Ｃの前面４Ｃ１及び後面４Ｃ２は中心
Ｐ３を中心とする半径Ｒ１，Ｒ２の円弧状に形成されて
いる。In the drawing, the front surface 4A1 and the rear surface 4A2 of the blade 4A in the rotation direction (indicated by the arrow) of the impeller 1 are formed into circular arc shapes with radii R1 and R2, respectively, centered on the same center P1. Similarly, the front surface 481 and the rear surface 4B2 of the blade 4B are formed in an arc shape with radii R1 and R2 similar to the above, centered on the center P2, and the front surface 4C1 and the rear surface 4C2 of the blade 4C are formed in an arc shape with radii R1 and R2 centered on the center P3. It is formed in the shape of a circular arc.
ここで中心Ｐ１．Ｐ２．Ｐ３は主盤２の中心Ｃを中心と
する円Ｅ上に等間隔で位置しており、これによって各羽
根４Ａ、４Ｂ、４Ｃ間の流体通路６の幅は入口部７から
出口部８に至り徐々に狭くなる。Here, center P1. P2. P3 are located at equal intervals on a circle E centering on the center C of the main plate 2, so that the width of the fluid passage 6 between each blade 4A, 4B, and 4C extends from the inlet part 7 to the outlet part 8. gradually narrows.
また、このような円Ｅ上の各中心Ｐｉ、Ｐ２゜Ｒ３の位
置決めは、以下のようにして行われている。Moreover, the positioning of each center Pi, P2°R3 on the circle E is performed as follows.
まず各羽根４Ａ、４Ｂ、４Ｇ・・・の外周縁を定める円
Ｅ上に羽根の枚数に応じて等間隔に点Ｑ１゜Ｑ２．Ｑ３
・・・をとる。点Ｑ１と中心Ｃを結ぶ直線Ｓ１を描き、
次に点Ｑ１を中心として直線Ｓ１に対し時計方向に角度
α傾いた直線Ｔ１を描き、この直線Ｔ１と円Ｅとの交点
をＰｌと定める。点Ｑ２、Ｑ３についても同様にして直
線Ｔ２．Ｔ３・・・を描きそれらと円Ｅとの交点をＲ２
，Ｒ３・・・とする。First, on the circle E that defines the outer periphery of each blade 4A, 4B, 4G, etc., points Q1, Q2, etc. are placed at equal intervals according to the number of blades. Q3
Take... Draw a straight line S1 connecting point Q1 and center C,
Next, a straight line T1 is drawn that is inclined by an angle α clockwise with respect to the straight line S1 with the point Q1 as the center, and the intersection of this straight line T1 and the circle E is determined as Pl. Similarly, for points Q2 and Q3, straight line T2. Draw T3... and set the intersection between them and circle E as R2
, R3...
また、特に本実施例において、各羽根４Ａ、４Ｂ、４Ｃ
・・・のボス２側の端部９は上記したようにボス２側に
至り徐々に狭くなるように構成されており、この構成は
各羽根４Ａ、４Ｂ、４Ｃ・・・の前面４Ａ１．４８１．
４Ｃ１・・・の端部９に対応する部分４Ａ１１．４Ｂ１
１．４Ｃ１１・・・を、部分４Ａ１１については前方に
位置する羽根４Ｆに関連する中心Ｐ６を中心とする半径
Ｒ３の円弧で、部分４Ｂ１１についても同様に前方に位
置する羽根４Ａに関連する上記中心Ｐ１を中心とする半
径Ｒ３の円弧で、部分４Ｃ１１についても前方に位置す
る羽根４Ｂの対応する中心Ｐ２を中心とする半径Ｒ３の
円弧でそれぞれ形成し、対応する前面４Δ１．４Ｂ１，
４０１・・・になだらかにつなげることで達成されてい
る。すなわち半径Ｒ３は上記半径Ｒ１よりも小さくなり
、端部９はボス２側に向けて先細状となる。In addition, especially in this embodiment, each blade 4A, 4B, 4C
As described above, the end portion 9 on the boss 2 side is configured to gradually become narrower toward the boss 2 side, and this configuration is similar to the front surface 4A1.481 of each blade 4A, 4B, 4C... ．．
Portion 4A11.4B1 corresponding to end 9 of 4C1...
1.4C11... is an arc of radius R3 centered on the center P6 related to the blade 4F located in the front for the portion 4A11, and the above center related to the blade 4A located in the front for the portion 4B11 as well. The portion 4C11 is also formed by an arc with a radius R3 centered on the corresponding center P2 of the blade 4B located at the front, and the corresponding front surface 4Δ1.4B1,
This is achieved by gently connecting to 401... That is, the radius R3 is smaller than the radius R1, and the end portion 9 is tapered toward the boss 2 side.
なお本実施例のインペラ１の各部の仕様は以下のようで
ある。Note that the specifications of each part of the impeller 1 of this embodiment are as follows.
主盤３の直径 １１９ｍ目玉５の外径
５６８円Ｅの直径
４８履羽根４の厚さ（ｆｆａ部９部外以外Ｍ
Ｒ１（羽根４の前面の曲率半径） ４５履Ｒ２（羽根４
の後面の曲率半径） ４１ｓＲ３（羽根４のボス２側
の端部９２６＃の前面の曲率半径）
角度α １４゜本実施例にお
いて、羽根４〜４の幅は主盤３と鋳造により一体で成形
されるため、比較的大寸法となっている。しかしながら
、各羽根４の端部９１１：
の厚さはボス２側に向けて先細状となっているため、流
体は端部９により流れを妨げられることなく目玉部５よ
り流体通路６の入口部９内に円滑に流入する。Diameter of main panel 3: 119 m Outer diameter of centerpiece 5: 568 yen Diameter of E
48 Thickness of shoe blade 4 (other than ffa part 9 M R1 (radius of curvature of front surface of blade 4) 45 Shoe R2 (blade 4
Radius of curvature of the rear surface) 41sR3 (Radius of curvature of the front surface of the end 926# on the boss 2 side of the blade 4) Angle α 14° In this example, the width of the blades 4 to 4 is formed integrally with the main plate 3 by casting. Therefore, it is relatively large in size. However, since the thickness of the end portion 911 of each blade 4 is tapered toward the boss 2 side, the fluid flows from the center portion 5 to the entrance portion of the fluid passage 6 without being hindered by the end portion 9. It flows smoothly into 9.
従って羽根４〜４が比較的大きな幅を有していた場合に
おいても本インペラ１の採用により先に説明した本出願
人による特願昭第６１−０５３３６９号と同様に優れた
揚程及び効率を備えたポンプを構成できる。Therefore, even if the blades 4 to 4 have a relatively large width, by adopting the present impeller 1, the same excellent head and efficiency as in Japanese Patent Application No. 61-053369 filed by the present applicant described above can be achieved. pumps can be configured.
次に本発明の第２実施例を第４図及び第５図を参照して
説明する。なお、本実施例は目玉部が小さなインペラに
関するもので、基本的な構造は第１実施例と同様であり
、同様な部材には同一符号を付してその説明を省略する
。Next, a second embodiment of the present invention will be described with reference to FIGS. 4 and 5. Note that this embodiment relates to an impeller with a small eye, and the basic structure is the same as that of the first embodiment, so similar members are given the same reference numerals and explanations thereof will be omitted.
第４図に示した本実施例のインペラ１３の羽根１４〜１
４は上記第１実施例の羽根４〜４と同様に羽根１４〜１
４の間に形成される流体通路１６の幅が入口部１７から
出口部１８に至り徐々に小さくなるように設定されてお
り、また各羽根１４はその全長に至り同一幅を有してい
るが、ボス２側の端部１９のみはボス２側に向かうにつ
れ徐々に厚さが小となる構成となっている。Blades 14 to 1 of the impeller 13 of this embodiment shown in FIG.
4 denotes blades 14 to 1 similar to blades 4 to 4 in the first embodiment.
The width of the fluid passage 16 formed between the blades 14 is set to gradually decrease from the inlet portion 17 to the outlet portion 18, and each blade 14 has the same width throughout its entire length. The thickness of only the end portion 19 on the boss 2 side gradually decreases toward the boss 2 side.
しかしながら、本実施例の羽根１４〜１４は上記第１実
施例の羽根４〜４に比べて半径方向内側（ボス２側）に
長く延びている。このためボス２との間の目玉部１５は
上記第１実施例の目玉部５よりも半径方向の幅が狭くな
っている。これに関連してボス２側の端部１９のインペ
ラ１３の回転方向に関し前方の面（後述する１４Ａ１１
．１４８１１．１４Ｃ１１・・・）は上記第１実施例の
対応する前方の面４Ａ１１．４Ｂ１１．４Ｃ１１・・・
とは異なる描き方で形成されている。However, the blades 14 to 14 of this embodiment extend longer inward in the radial direction (towards the boss 2) than the blades 4 to 4 of the first embodiment. Therefore, the width of the eyelet portion 15 between the boss 2 and the boss 2 in the radial direction is narrower than that of the eyeball portion 5 of the first embodiment. In connection with this, the front surface of the end 19 on the boss 2 side with respect to the rotation direction of the impeller 13 (14A11 described later)
．． 14811.14C11...) corresponds to the corresponding front surface 4A11.4B11.4C11... of the first embodiment.
It is drawn in a different way.
以下上記のような羽根１４〜１４の具体的な形状及び配
置を第５図を参照して詳しく説明する。The specific shape and arrangement of the blades 14 to 14 as described above will be explained in detail below with reference to FIG. 5.
図中円弧Ｅ１は第１実施例の円弧Ｅに対応するもので、
円弧Ｅ１上には羽根１４Ａの前面１４Ａ１及び後面１４
Ａ２の中心Ｐ１１、羽根１４８の前面１４Ｂ１及び後面
１４Ｂ２の中心Ｐ１２、羽根１４Ｇの前面１４Ｃ１及び
後面１４Ｃ２の中心Ｐ１３・・・が等間隔で位置してお
り、各羽根１４Ａ。The arc E1 in the figure corresponds to the arc E in the first embodiment,
On the arc E1 are the front surface 14A1 and the rear surface 14 of the blade 14A.
The center P11 of A2, the center P12 of the front surface 14B1 and rear surface 14B2 of the blade 148, and the center P13 of the front surface 14C1 and rear surface 14C2 of the blade 14G are located at equal intervals, and each blade 14A.
１４８．１４０・・・間の流体通路１６の幅は入口部１
７から出口部１８に至り徐々に狭くなっている。148, 140... The width of the fluid passage 16 between the inlet portion 1
7 to the outlet section 18, which gradually becomes narrower.
なお円Ｅ１の半径は上記１実施例の円Ｅの半径よりも僅
かに大きく設定されており、円Ｅ１上の各中心Ｐ１１．
Ｐ１２．Ｐ１３・・・の位置決めは、先の実施例の直線
Ｔ１．Ｔ２．Ｔ３・・・に対応する直線Ｔ１１．Ｔ１２
．Ｔ１３・・・を描いてそれらの円Ｅ１との交点を中心
Ｐｉ １．Ｐｌ ２．Ｐｌ ３・・・としである。Note that the radius of the circle E1 is set slightly larger than the radius of the circle E in the first embodiment, and each center P11 .
P12. P13... is positioned using the straight line T1. in the previous embodiment. T2. Straight line T11. corresponding to T3... T12
．． Draw T13... and set the intersection point with the circle E1 as the center Pi 1. Pl 2. Pl 3...This is Toshishita.
また、本実施例の、各羽根１４Ａ、１４Ｂ、１４Ｃ・・
・の前面１４Ａ１．１４Ｂ１．１４Ｃ１・・・のボス２
側の端部１９に対応する部分１４Ａ１１゜１４Ｂ１１．
１４Ｃ１１・・・は、上記円Ｅ１と同心でこれよりも半
径が僅かに小さな円Ｅ２上の等間隔の点Ｕ１．Ｕ２．Ｕ
３・・・を中心とする半径Ｒ１３の円弧状に形成されて
いる。ここで、点Ｕ１は前方に位置する羽根１４Ｆに関
連する直線Ｔ１６と円Ｅ２との交点、点Ｕ２も同様に前
方に位置する羽根１４Ａ１．：関連する直線Ｔ１１と円
Ｅ２との交点、点Ｕ３も前方に位置する羽根１４Ｂに関
連する直線Ｔ１２と円Ｅ２との交点というように順次決
定されている。In addition, each blade 14A, 14B, 14C of this embodiment...
・Front surface 14A1.14B1.14C1...Boss 2
The portion corresponding to the side end 19 14A11°14B11.
14C11... are equally spaced points U1... on a circle E2 that is concentric with the circle E1 and has a slightly smaller radius than the circle E1. U2. U
3... is formed in an arc shape with a radius R13 as the center. Here, the point U1 is the intersection of the straight line T16 and the circle E2 related to the blade 14F located at the front, and the point U2 is also the intersection of the blade 14A1 located at the front. : The intersection point between the related straight line T11 and the circle E2, and the point U3 are also determined as the intersection point between the straight line T12 and the circle E2 related to the blade 14B located in the front, and so on.
なお本実施例のインペラ１３の各部の仕様は以下のよう
である。（記載のない部位の仕様は上記第１実施例と同
様である。Note that the specifications of each part of the impeller 13 of this embodiment are as follows. (Specifications of parts not described are the same as in the first embodiment.
目玉１５の外径 ４８ａａ＋円Ｅ１の
直径 ４２麿円Ｅ２の直径
４０Ｍ１羽根１４の前面の曲率半径
４２ｍ羽根１４の後面の曲率半径 ３８履Ｒ１
３（羽根１４のボス２側の ２２Ｍ１端部１９の前面
の曲率半径）
本実施例の作用は上記第１実施例と同様であるが、前面
１４Ａ１．１４Ｂ１．１４Ｃ１・・・を描くための円Ｅ
１と部分１４Ａ１１．１４Ｂ１１，１４Ｃ１１・・・を
描くための円Ｅ２を異ならせることにより、羽根１４Ａ
、１４Ｂ、１４Ｇ・・・の長さ、目玉１５の幅に応じて
、部分１４Ａ１１．１４Ｂ１１．１４Ｃ１１・・・が前
面１４Ａ１．１４８１゜１４０１・・・になだらかにつ
ながるように形成できる。Outer diameter of eyeball 15 48aa + diameter of circle E1 42maro diameter of circle E2
Radius of curvature of the front surface of 40M1 blade 14
Radius of curvature of the rear surface of the 42m blade 14: 38mm R1
3 (radius of curvature of the front surface of the 22M1 end 19 on the boss 2 side of the blade 14) The operation of this embodiment is similar to that of the first embodiment, but the circle for drawing the front surface 14A1.14B1.14C1... E
1 and the parts 14A11, 14B11, 14C11... By making the circle E2 different for drawing the parts 14A11, 14B11, 14C11...
, 14B, 14G... and the width of the eyeball 15, the portions 14A11.14B11.14C11... can be formed to smoothly connect to the front surface 14A1.1481°1401....
なお、第２実施例は羽根１４Ａ、１４Ｂ、１４Ｃ・・・
の長さが第１実施例の羽根４Ａ、４Ｂ、４Ｃ・・・より
も良く、目玉１５が第１実施例の目玉５よりも幅狭の場
合に関連して説明したが、逆に第１実施例のものよりも
羽根が長く、目玉の幅が広い場合には、例えば上記円Ｅ
２の半径を円Ｅ１よりも大きく設定することで前面１４
Ａ１．１４Ｂ１゜１４Ｃ１・・・になだらかにつながる
部分１４△１１゜１４Ｂ１１，１４Ｃ１１・・・を容易
に形成できる。In addition, in the second embodiment, the blades 14A, 14B, 14C...
The length of the blades 4A, 4B, 4C, etc. of the first embodiment is better than that of the first embodiment, and the eyeball 15 is narrower than the eyeball 5 of the first embodiment. If the wings are longer than those in the example and the eyeball is wider, for example, the above circle E
By setting the radius of 2 to be larger than the circle E1, the front surface 14
The portions 14Δ11°14B11, 14C11... that smoothly connect to A1.14B1°14C1... can be easily formed.
（発明の効果）
本発明において流体はボス側から各羽根の間の入口部に
流入するに際し羽根のボス側の端部により流れが妨げら
れることなく円滑に流入できるので、例えば羽根がｌｉ
ｔ造や樹脂成形によりインペラと一体で形成される場合
のように羽根の厚さが比較的厚い場合でも、インペラの
重量バランスが良く、優れた揚程及び効率が得られるポ
ンプやコンプレッサを提供できる利点を有する。(Effects of the Invention) In the present invention, when fluid flows from the boss side to the inlet portion between each blade, the flow can be smoothly flowed in without being obstructed by the end of the blade on the boss side.
The advantage is that even when the blades are relatively thick, such as those formed integrally with the impeller by T construction or resin molding, the impeller has a good weight balance and can provide pumps and compressors with excellent head and efficiency. has.
第１図〜第３図は本発明の第１実施例の流体灘械用イン
ペラを示すもので、第１図はインペラの正面図、第２図
は第１図のｎ−ＩＩ線に沿う断面図、第３図は第１図に
示したインペラにおける羽根の位置決めの様子を図解す
る説明図、第４図及び第５図は本発明の第２実施例を示
づもので、第４図はインペラの正面図、第５図は第４図
に示したインペラの第３図と同様な説明図、第６図は従
来のインペラの正面図である。
１．１３・・・インペラ ２・・・ボス３・・・主盤
４．４八〜４Ｆ、１４．１４Ａ〜１４Ｆ・・・羽根
５．１５・・・目玉 ６，１６・・・流体通路９．
１９・・・端部1 to 3 show an impeller for a hydrodynamic machine according to a first embodiment of the present invention, FIG. 1 is a front view of the impeller, and FIG. 2 is a cross section taken along the line n-II in FIG. Figures 3 and 3 are explanatory diagrams illustrating the positioning of the blades in the impeller shown in Figure 1, Figures 4 and 5 show a second embodiment of the present invention, and Figure 4 shows 5 is a front view of the impeller, FIG. 5 is an explanatory view similar to FIG. 3 of the impeller shown in FIG. 4, and FIG. 6 is a front view of a conventional impeller. 1.13...Impeller 2...Boss 3...Main board 4.48~4F, 14.14A~14F...Blade 5.15...Eyeball 6,16...Fluid passage 9 ．．
19... end
Claims (1)
一方の側面から前記ボスの軸方向に突出する円周方向等
間隔に配置された複数の羽根とを有し、これらの羽根は
隣り合う各羽根との間に前記ボスのまわりから前記主盤
の外周部に至る流体通路を形成し、かつこれらの流体通
路はその断面積が前記ボスのまわりから前記主盤の外周
に向って徐々に小さくなるように構成され、前記主盤の
回転により前記ボスのまわりの流体を前記流体通路を経
て前記主盤の外周方向に導くようにした流体機械用イン
ペラであつて、前記羽根の円周方向の厚さ寸法を前記ボ
スに近接する部位を除き全長に亘りほぼ均一に形成し、
その前記ボスに近接する部位の厚さを前記ボス側に向け
て徐々に小さくなるように構成したことを特徴とする流
体機械用インペラ。It has a main plate having a boss in the center, and a plurality of blades that protrude from at least one side of the main plate in the axial direction of the boss and are arranged at equal intervals in the circumferential direction, and these blades are adjacent to each other. A fluid passage from around the boss to the outer periphery of the main plate is formed between each blade, and the cross-sectional area of these fluid passages gradually increases from around the boss to the outer periphery of the main plate. The impeller for a fluid machine is configured to be smaller in size and is configured to guide fluid around the boss through the fluid passage toward the outer circumferential direction of the main disk by rotation of the main disk, the impeller being configured to be smaller in size in the circumferential direction of the blade. The thickness dimension is formed almost uniformly over the entire length except for the portion close to the boss,
An impeller for a fluid machine, characterized in that the thickness of a portion close to the boss gradually decreases toward the boss.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP26958889A JPH03130598A (en) | 1989-10-16 | 1989-10-16 | Impeller for fluid machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP26958889A JPH03130598A (en) | 1989-10-16 | 1989-10-16 | Impeller for fluid machine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH03130598A true JPH03130598A (en) | 1991-06-04 |
Family
ID=17474451
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP26958889A Pending JPH03130598A (en) | 1989-10-16 | 1989-10-16 | Impeller for fluid machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH03130598A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5620306A (en) * | 1992-11-12 | 1997-04-15 | Magiview Pty. Ltd. | Impeller |
| JP2000145685A (en) * | 1998-11-12 | 2000-05-26 | Kubota Corp | Centrifugal blower |
| WO2005003567A1 (en) * | 2003-07-02 | 2005-01-13 | Yukinori Sakata | Centrifugal impeller and method of designing the same |
| JP2013501521A (en) * | 2009-08-14 | 2013-01-17 | エス．シー． ジョンソン アンド サン、インコーポレイテッド | Wearable chemical dispenser |
| JP2013015101A (en) * | 2011-07-05 | 2013-01-24 | Ihi Corp | Centrifugal compressor |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2165808A (en) * | 1937-05-22 | 1939-07-11 | Murphy Daniel | Pump rotor |
| JPS62210297A (en) * | 1986-03-11 | 1987-09-16 | Eiichi Sugiura | Impeller for rotary type fluid machine |
-
1989
- 1989-10-16 JP JP26958889A patent/JPH03130598A/en active Pending
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2165808A (en) * | 1937-05-22 | 1939-07-11 | Murphy Daniel | Pump rotor |
| JPS62210297A (en) * | 1986-03-11 | 1987-09-16 | Eiichi Sugiura | Impeller for rotary type fluid machine |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5620306A (en) * | 1992-11-12 | 1997-04-15 | Magiview Pty. Ltd. | Impeller |
| JP2000145685A (en) * | 1998-11-12 | 2000-05-26 | Kubota Corp | Centrifugal blower |
| WO2005003567A1 (en) * | 2003-07-02 | 2005-01-13 | Yukinori Sakata | Centrifugal impeller and method of designing the same |
| JP2013501521A (en) * | 2009-08-14 | 2013-01-17 | エス．シー． ジョンソン アンド サン、インコーポレイテッド | Wearable chemical dispenser |
| JP2013015101A (en) * | 2011-07-05 | 2013-01-24 | Ihi Corp | Centrifugal compressor |
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