JPS5818592A - Single blade type turbine pump - Google Patents

Abstract

PURPOSE:To reduce vibration and to aim at reducing the weight of a turbine by adjusting the thickness of a blade for the balancing with respect to the axial center of the pump and the axis orthogonal to the pump axis. CONSTITUTION:The thickness of a blade 2 is adjusted so that the static balance with respect to the center line 3 satisfies the relation, SIGMAMA'=SIGMAMB', where MA', MB' are moments of the mass of infinitesimal portions A', B' about the center line 3. For the static balance with respect to the axial center 0' vertical to the center line 3, the thickness of the blade 2 is adjusted so that the integral of a moment of an infinitesimal part C' of the blade 2 within an infinitesimal angle DELTAtheta having a momentum arm in the direction of the center line 3 with respect to the axial center 0', to the integral of an infinitesimal part D' having a momentum arm in the direction of the center line 3 with respect to the axial center 0', over an angle theta.

Description

【発明の詳細な説明】 ンプに関する。[Detailed description of the invention] Regarding the pump.

汚水、汚物、パルプ液等Ｑ移送用ポンプとしては固形物
、繊維物質等の異物が詰ったシ、引っ掛った〕すゐこと
のな１無閉塞性のポンプが要求される。この種のボ／グ
としては一枚又は小数枚の翼を持つ羽根車を備えたもの
がある。As a pump for transporting sewage, filth, pulp liquid, etc., a non-obstructive pump is required that will not be clogged or caught by foreign matter such as solid matter or fibrous matter. This type of bo/g has an impeller with one or a few blades.

第６図は従来例の小数枚の翼を備えたポンプの例である
．図において翼コを備えた羽根車／は図示する中心線３
を中心に回転するようポンプケーシタグａｌ１ｃ支持さ
れてｉる。ポンプケーシタグダと翼一〇縁辺との間に図
示１の間隙がある。Figure 6 is an example of a conventional pump with a small number of blades. In the figure, the impeller with blades / is the center line 3 shown in the figure.
The pump casing tag al1c is supported so as to rotate around the center. There is a gap 1 shown in the figure between the pump casing tag and the edge of the blade 10.

第７図は第１図の羽根車の一部正面図である。FIG. 7 is a partial front view of the impeller shown in FIG. 1.

翼一の翼端５は中心１１１３よりの放射線の方向よシ角
！後退し九位置にある。このような例ではだ液体が流れ
ゐため、間隙一の部分に固形物等が入っても間隙δが太
き一から通過し得るｏしかし乍らこの構造では液の漏洩
損失が大きく、従ってポンプ効率を低下せしめる。The tip 5 of the first wing is at an angle to the direction of the radiation from the center 1113! Backed up and in the 9th position. In such an example, liquid is flowing, so even if a solid object enters the gap 1, it can pass through the gap δ, which is wide. However, with this structure, the leakage loss of liquid is large, and therefore the pump Reduces efficiency.

他の従来例としては母線が直線、曲線の円錐形回転面を
なすポンプケーシングとねじ羽根の翼の外周回転面が同
円錐形回転面の羽根車を備えたものがある（＋ｌＩ会昭
−３−／１００＆）。この会知例のポンプは円錐様の第
一ハブに第一〇へプＯ軸に対し角度がずれてしる第二の
ハブを備えて第一、第二のハブを取巻き第二の軸のずれ
たハブから軸方向に上流に延びた略一定の厚みをもつ九
単−の連続し九螺旋形のねじ板を備えた羽根車がケーシ
ング中ＫＩＩ間少く納められている◎この種のポンプで
はねじ羽根を第一ハブより先に出すこ々によ）ポンプ性
能の向上が認められる一方、このように第二のハブを延
出してねじ羽根先端を補強しなければならずこのように
補強したとしてもねじ羽根先端は弱く、剛性は低く振動
を発生する原因となる。又、ねじ羽ＩＮ（ねじ徹）が一
様な厚さであるため羽根車自体が不平衡重量を備えてお
）、ポンプの振動の原因ともなって−る・これらの振動
を防止するため円錐様ハブ根本内側を研削して落して軸
を太くして対応して匹る現状にある。Another conventional example includes a pump casing whose generating line is a straight line and a curved conical rotating surface, and an impeller whose outer circumferential rotating surface of the screw blade blade is the same conical rotating surface (+lI Kaisho-3 -/100&). The pump of this known example has a conical first hub and a second hub that is angularly shifted from the first and second hubs, and the second hub surrounds the first and second hubs and is connected to the second shaft. An impeller with a continuous nine-helical screw plate of approximately constant thickness extending axially upstream from the offset hub is housed in the casing. While it is recognized that pump performance is improved by extending the screw blades before the first hub, it is necessary to extend the second hub in this way and reinforce the tip of the screw blades. However, the tip of the screw blade is weak and has low rigidity, causing vibration. In addition, since the screw impeller IN has a uniform thickness, the impeller itself has an unbalanced weight, which causes vibrations in the pump.In order to prevent these vibrations, the impeller itself has a conical shape. The current situation is to grind down the inside of the hub base and make the shaft thicker.

そこで第一の従来例にあるような羽根車の翼端の流れを
中心に向は得て、固定物を中心に向けて移動させ、且つ
第二の従来例にあるよ５な強度、剛性上の問題点を解決
し得るような一枚翼の無閉塞性ボ／グを得ることを目的
とした特願昭３６−４６０３！号に係わる発明「一枚翼
羽根車ポｙプ」は、 「　吸込口と吐出ケーシング間が円錐様回転面をなした
ポンプケーシングに、外周回転胃がポンプケーシングの
円錐様回転面に隙間少く接近する円錐様をなしたねじ羽
根の翼を円錐様ハブに形成した羽根車をケージング内に
て回転可能に支持した一枚翼羽根車ポンプにお−て、吸
込側翼根本を円錐様ハブ頂点近傍にて終らせた該翼根率
よりポンプ軸中心線よシの放射線よりも翼端正面が前進
する方向に翼端を傾けた一枚翼羽根車ポｙグ、」 であって、翼根率を円錐様ハブ先端近傍（て終らせて、
翼端を翼端前進側へ傾けて設けたから、闇彫物が羽根車
先端にて中心に向う。翼は根本が円錐様ハブ先端近傍に
て終って−るので強固で剛性があシ、翼自体振動しＪＩ
Ｉｖｈ０又、翼厚を不平衡重量をなくするよう変化させ
たから、従来の一枚翼の羽根車のようにある決った外径
のものでのみバランスして居夛、ポンプ要項（流量、揚
程）が変った場合、通常の遠心ポンプの羽根車のように
外径加工ができず（不平衡重量が生じる）、ベルト駆動
等の回転数変換に頼らざるを得ないと９５点がな（なシ
応用範囲が広くなって−る。Therefore, as in the first conventional example, the direction is obtained around the flow at the blade tip of the impeller, and the fixed object is moved toward the center, and the strength and rigidity are improved as in the second conventional example. A patent application filed in 1973-4603 aimed at obtaining a single-winged non-obstructive bore that could solve the problems of the above! The invention ``Single-blade impeller pump'' is based on ``a pump casing in which a conical rotating surface is formed between the suction port and the discharge casing, and an outer circumferential rotating stomach approaches the conical rotating surface of the pump casing with little clearance. In a single-blade impeller pump, in which an impeller with conical screw blades formed on a conical hub is rotatably supported in a casing, the root of the suction side blade is placed near the apex of the conical hub. A single-blade impeller whose blade tip is inclined in the direction in which the front surface of the blade moves forward from the line of the center line of the pump shaft, with the blade root ratio Near the tip of the conical hub (ending at
Since the wing tips are tilted toward the forward wing tip side, the dark carvings are directed towards the center at the tip of the impeller. The blade's root ends near the tip of the conical hub, so it is strong and rigid, and the blade itself vibrates.
Ivh0 Also, since the blade thickness is changed to eliminate unbalanced weight, the pump requirements (flow rate, head) can be balanced only with a certain outer diameter, like a conventional single-blade impeller. If the impeller of a centrifugal pump changes, the outer diameter cannot be machined like the impeller of a normal centrifugal pump (unbalanced weight occurs), and the number of rotations must be changed by belt drive etc. The range of applications is expanding.

処がこの第三の発明の一枚翼羽根車ポンプでは効率が従
来例に比して良好ではあっても極めて良好とは−えず歯
高効率化を計る必要が奉る。However, although the efficiency of the single-blade impeller pump of the third invention is better than that of the conventional example, it is not extremely good; therefore, it is necessary to improve the efficiency of the tooth height.

そして第三の発明にシける翼のバランスは立体上のもの
を平置上に投影して不釣合をなくしようとするものであ
るため軸方向の釣合がとれて訃らず淘充分とは一見なｉ
ものである。The balance of the wing in the third invention is to eliminate unbalance by projecting a three-dimensional object onto a flat surface, so at first glance it seems that the balance in the axial direction is maintained and it is sufficient to prevent it from collapsing. na i
It is something.

本発明の第１の目的は一枚翼羽根車ポンプの効率の向上
を計ることであシ、本発明の他の目的は円錐様回転面に
ねじ羽根の翼の外周があるような羽根車の重量の不平衡
を完全に除き得るよ５なねじ羽根の翼形状を得ることで
ある。A first object of the present invention is to improve the efficiency of a single-blade impeller pump, and another object of the present invention is to improve the efficiency of a single-blade impeller pump. The objective is to obtain a screw blade shape that can completely eliminate weight imbalance.

本発明の一枚翼羽根車ポングは翼の厚さが羽根車回転中
心を直交してとおる直線上に存在する翼の部分が回転中
心に対して等しいモーメントを持つように翼厚を変える
と共に、羽根車の支持部をとお夛回転中心Ｋ［交する軸
に対する軸方向距離をアームとする前記翼の部分のモー
メントの合計が零となるように翼厚を変化させてなる一
枚翼羽根車ボ／グである。The single-blade impeller pong of the present invention changes the blade thickness so that the portion of the blade that lies on a straight line passing orthogonally to the impeller rotation center has an equal moment with respect to the rotation center, and The support part of the impeller is set at the center of rotation K [the axial distance from the intersecting axes is the arm], and the blade thickness is changed so that the sum of the moments of the blade parts becomes zero. /G.

以下、図面に従って本発明の実施例につ−て説明する。Embodiments of the present invention will be described below with reference to the drawings.

第１図は本発明のポンプ軸を含む縦断面図である。ポン
プケーシタグダは吸込口６が一体に形成せられ、吸込口
６側を小端として内周は直線又は曲線もしくはそれらを
組合せた母線をポンプ主軸３′を中心にして回転させた
円錐様形状であ）、ポンプケーシタグダには吐出ケーシ
タグクが固定され、吐出ケーシタグクに軸方向移動を制
止され、回転可能に軸承され軸封（説明は省略する）さ
れ九ボ／グ主軸３′には羽根車ｌの円錐様ハブｌがポン
プ主軸３′の締シ勝手方向になるようＫねじ込まれてい
る。円錐様ハブｔは母線が直線又は曲線又はそれらを組
合せた回転−面であ）、ポンプケーシタグダとの間の流
体通路が適当になるよ５に選ばれている。FIG. 1 is a longitudinal sectional view including the pump shaft of the present invention. The pump casing tag is integrally formed with the suction port 6, and has a cone-like shape with the suction port 6 side as the small end and the inner circumference rotated around the pump main shaft 3' with a generatrix of a straight line, a curve, or a combination thereof. ), a discharge casing tag is fixed to the pump casing tag, axial movement is restrained by the discharge casing tag, rotatably supported and shaft sealed (description will be omitted), and a blade is mounted on the main shaft 3' of the pump casing. The conical hub 1 of the wheel 1 is screwed into the pump main shaft 3' so that it is in the tightening direction. The conical hub t has a generatrix of a straight line, a curved line, or a rotating surface with a combination thereof, and is selected to have an appropriate fluid passage between the hub and the pump casing.

円錐様ハブＨｃはねじ羽根の翼−２Ｊ）！一体に形成せ
られてｉる。翼コの吸込口１の側は円錐様ハブｔの頂点
附近もしくは頂点で終っておシ、その位置よシ翼端！が
翼−の外周に向う。翼コの外周はポンプクーシングヂの
内周面と隙間少な一位置ＫＩｈる直線又は曲線もしくは
これらを組合せた母線を有する軸３′を中心とする回＠
藺上にある。The conical hub Hc is a screw blade wing - 2J)! It is integrally formed. The suction port 1 side of the wing ends near or at the apex of the conical hub t, and that position is the wing tip! toward the outer circumference of the wing. The outer periphery of the blade rotates around an axis 3' having a straight line, a curved line, or a generatrix of a combination of these, which is located at a position KIh with a small clearance from the inner circumferential surface of the pump cushioning.
It's on point.

第１図は翼コの先端中心部の拡大正面図である・円錐様
ハブｌと翼コの根本の境界線デは中心線３（紙面に直交
している）近傍にて終っており、中心ＩＩＪよりの放射
線１０よシ翼端ｊが進んで行く方向に翼端！は放射線１
０よシ次第に離れて行くような凹な曲線をなしている。Figure 1 is an enlarged front view of the center of the tip of the wing. The boundary line between the conical hub l and the root of the wing ends near the center line 3 (orthogonal to the plane of the paper), and the center Radiation 10 from IIJ and the wing tip in the direction in which the wing tip j advances! is radiation 1
It forms a concave curve that gradually moves away from 0.

これは曲率が太き−ときは直線に代えてもよいが後に説
明される流体の流れを中心に向けるように図のような中
心より離れるに従って切線角ｒが次第に大となる曲線が
望ましい。中心線３と翼端５と翼−の外周ｌ／との交点
／Ｊとを結ぶ線と放射線１０が中心線３に張る角αは図
示冥例の大きさである。This may be replaced with a straight line if the curvature is thick, but it is preferable to use a curved line in which the tangential angle r gradually increases as the distance from the center increases as shown in the figure so as to direct the flow of fluid toward the center, which will be explained later. The angle α between the center line 3 and the line connecting the center line 3 and the intersection /J of the blade tip 5 and the outer circumference l/ of the blade and the ray 10 is the size of the illustrated example.

第３図は羽根車／の略正面図である。図におμて説明の
ため中心線３を原点としてＸ、Ｙ座標軸を設けである。FIG. 3 is a schematic front view of the impeller. In the figure, for explanation purposes, X and Y coordinate axes are provided with the center line 3 as the origin.

今、翼−の厚さを同一とすると、右上を第一象限として
左回シに見て第三、第四象限の翼１の各部を中心線Ｊを
とおる直−につｉて対抗した中心Ｉ！３につめての一次
＋　−メントは明かに第三象限、第四象限の翼シが小さ
ｉ・従って翼厚が一定とすると不平衡重量を生ずる。そ
こでこの実施例では第３図に示され、又翼コの展開した
外周縁側よシ見九第ゲ図に示されるように中心線ＪＫつ
−て１次モーメンＦが等しくなるように第三、第四象限
にある翼コＯ翼厚を変化させである。この翼−の肉厚を
厚くする部分は第４ｔＷＪに誇張して示されるように翼
コの裏側７３であって流体に作用する表側は流体力学的
に適する面としておく。この不釣合重量に関しては更に
後にのべるＯ 第を図は羽根車ｌの翼−の吸込口側よ）見る正面図であ
って翼コのおもて側シェラウド側角が示されて−る。第
デ図は第を図における中心線を含む羽根車／の断面図で
ある。Now, assuming that the thickness of the wing is the same, the upper right corner is the first quadrant, and each part of the wing 1 in the third and fourth quadrants when viewed from the left is the center opposed to the center line i through the center line J. I! In the third primary + -ment, the blades in the third and fourth quadrants are clearly small i. Therefore, assuming that the blade thickness is constant, unbalanced weight will occur. Therefore, in this embodiment, as shown in Fig. 3 and also shown in Fig. 9 when viewed from the outer peripheral edge side where the wing is expanded, the third The thickness of the blade in the fourth quadrant is changed. The part where the wall thickness of the blade is increased is the back side 73 of the blade, as shown exaggeratedly in the fourth tWJ, and the front side that acts on the fluid is a hydrodynamically suitable surface. This unbalanced weight will be discussed further below.The figure is a front view looking from the suction port side of the blade of the impeller l, and shows the front side corner of the shroud of the blade. Figure D is a sectional view of the impeller including the center line in Figure D.

第を図の真コの吸込口側の翼端のＱ−ａ断面翼コ・で表
わされる。翼コａの所間の厚さはシ具ツウド儒１／、翼
根本儒を−とするとｔｌ−ｔｌ即ち平板状でわる・ 翼−と円錐様ハブｌとの取付角α、即ち翼コのおもて側
とポンプ主軸３′の中心線３とのなす角αは入口側の翼
Ｊ＆にてはαｍ５ｏ−４ａｙであ夛出口側の翼コ・にて
はα＝０〜ダ０［であル、入口側よ）出口側に向って角
αは次第に小となってｉる。The number is represented by the Q-a cross section of the blade tip on the suction port side of the figure. If the thickness of the wing core a is 1/, and the base thickness of the wing is -, then it is tl - tl, that is, it is a flat plate. The angle α between the front side and the center line 3 of the pump main shaft 3' is αm5o-4ay for the blades J& on the inlet side, and α=0~da0[ for the blades J& on the outlet side. (That's the entrance side) The angle α gradually becomes smaller towards the exit side.

以上に対して従来例の一枚翼羽根車ポンプの翼の上記諸
元は第を図の断面線を第１０図で示すような翼断面を有
し、入口部の翼−２＆の翼厚１／（１−であり、翼取付
角α＝ｓｏ〜６０ｆであって入口側の翼コａよシ出ロ側
の翼−ｅｔで一定である。In contrast to the above, the above specifications of the blade of the conventional single-blade impeller pump have a blade cross section as shown in Figure 10, and the blade thickness of the inlet part is 1. /(1-, and the blade attachment angle α=so~60f, which is constant between the blade A on the inlet side and the blade -et on the exit side.

第１図において羽根車ｌが回転すると固形物を含んだ流
体は吸込まれ、ポンプケーシング夢中で翼−の９間を移
動して吐出ケーシタグクに送られ吐出される。その際、
第３図の説明図に示されるように翼端ｊの部分で固形物
等は矢印ｌ＃の方向に流れる。円錐様ハブｔの先端は図
示されてはしるが翼コの厚さにより実際にはなく、翼端
Ｓは円錐様）１プｔに滑かに連続しているから、翼コと
円錐様ノ）プを及びポンプケーシタグダ間の空間に障害
なく入る。かくして固形物等を含む液体も翼１外周とボ
ンプケーシタグダ間の隙間につまることなく送られる。In FIG. 1, when the impeller l rotates, fluid containing solids is sucked in, moves between the blades of the pump casing, is sent to the discharge casing, and is discharged. that time,
As shown in the explanatory view of FIG. 3, solid matter and the like flow in the direction of arrow l# at the blade tip j. Although the tip of the conical hub t is shown in the figure, it is not actually present due to the thickness of the wing, and the wing tip S smoothly continues to the conical hub. into the space between the pump and the pump casing without obstruction. In this way, liquid containing solid matter and the like is also sent to the gap between the outer periphery of the blade 1 and the bomb case tag without clogging it.

即ち、本発明の一枚翼羽根車ポンプ４従来例も同様に動
作する・こ−Ｋか−で入口側の翼ｊａは一定厚さである
ことによ〕従来例に比して固型物等が滑らかく翼間に入
ることが判明した。That is, the conventional single-blade impeller pump 4 of the present invention operates in the same manner.In this case, the blades ja on the inlet side have a constant thickness. etc., it was found that it could smoothly fit between the wings.

第１１図は以上に説明した本発明の一枚翼羽根車ポンプ
と従来例のもののポンプ性能の比較を示す線図である。FIG. 11 is a diagram showing a comparison of the pump performance of the single-blade impeller pump of the present invention described above and the conventional pump.

横軸に吐出し量を縦軸には全揚程と効率をとったもので
、実線で示されるものは本発明の一枚翼羽根車ボｙ７′
に関するものであシ、点線は従来例に関するものである
。The horizontal axis shows the discharge amount, and the vertical axis shows the total head and efficiency.The solid line shows the single blade impeller body 7' of the present invention.
The dotted line is related to the conventional example.

図よ）明らかなように最大効率において本発明の一枚翼
羽根車ポンプのほうが従来例よシ改良されてｓＩ−，６
、その点における本発明の一枚翼羽根車ポンプの揚程を
■１１従来例のものをＨＪとするとＩＩ／／Ｈコｗｘｂ
−〜ｉ、ｓであった・このように本発明の一枚翼羽根車
ポングは従来例よ）％効率よく揚１大であるから、逆に
同揚程のものとするとポンプを小さくできる訳である。As is clear, the single-blade impeller pump of the present invention is improved over the conventional example in terms of maximum efficiency.
, In that respect, the head of the single-blade impeller pump of the present invention is II//H wxb, assuming that the conventional example is HJ.
- ~ i, s - In this way, the single-blade impeller pump of the present invention is 1% more efficient than the conventional example, so if it has the same head, the pump can be made smaller. be.

既に第３Ｗ１にお−てのべたように羽根車ｌは策されて
−る。処がポンプ主軸３′を含む縦断面図の第１Ｊ図に
示されるように翼コが軸方向に位置を変えながら渦巻状
〈なって−るから、第３図に示される釣合の取り方は第
１−図に示されるように中心線３を頂点とする対重な微
小角６０間に含まれる翼１の図示位置Ａ′の質量Δ１ｌ
ｌＬとｉｔθ０反対側の位置Ｂ′の質量Δｍｂを比較し
て釣合せている訳であるから、ポンプ軸３′の中心線Ｊ
上の点を第７−２図の紙面に直交して羽根車の支持部を
とおる軸心０／に関して不釣合を生ずる。The impeller l is designed as already mentioned in 3rd W1. However, as shown in Figure 1J, which is a longitudinal cross-sectional view including the pump main shaft 3', the blades are shaped like a spiral while changing their position in the axial direction, so the balance shown in Figure 3 is achieved. is the mass Δ1l of the blade 1 at the illustrated position A', which is included between the overlapping minute angles 60 with the center line 3 as the apex, as shown in FIG.
Since the balance is made by comparing lL with the mass Δmb at position B' on the opposite side of itθ0, the center line J of pump shaft 3'
An unbalance occurs with respect to the axis 0/, which passes through the support portion of the impeller with the upper point perpendicular to the paper plane of FIG. 7-2.

ＪＩ／Ｊ図に示されるよ５に中心線３に関しての微小部
分ム′、Ｂ′の質量の中心＠ｊについてのモーメントを
Ｍム′１ＭＢ′とすると中心１．７に対する静的の釣合
は Ｊ　Ｍ　、／−ΣＭＢＩ の関係となるよ５翼−２０肉厚は変化させると共に、第
７３図に示すように中心線３に対して直角な細心０７に
対する静的′つプ合をとるため、微小角Δθ内の翼コの
微小部分Ｃ′の軸心Ｏ′についての中心ｌＩＪ方向をア
ームとするモーメントを輩ｃ′、微小部分Ｄ′の軸心０
′につ１ての中心線３方向をアームとするモーメントを
ＭＤ′γとするとの関係となる様肉厚を変化させである
。この結果翼コの厚さは翼コの展開図の第グ図に示され
るよ５に入口側の厚さをｔｌ、出口側の厚さｔｏとする
と ｔ１≧−ｔｏ にとられることとなって−る。これらの翼形は翼表側は
流体力学的（定められ、真裏側をふくらませて形成され
て−る。As shown in the JI/J diagram, if the moment about the center of mass @j of the minute part M' and B' with respect to the center line 3 is M'1MB', the static balance with respect to the center 1.7 is In order to change the wall thickness of the 5-blade 20 so that the relationship is J M , /-ΣMBI, and to take the static 'fit for the fine center 07 perpendicular to the center line 3 as shown in Figure 73, The center of the minute part C' of the wing within a minute angle Δθ about the axis O' generates a moment with the arm in the IJ direction, and the axis 0 of the minute part D'
The wall thickness is changed so that the relationship is as follows, where MD'γ is the moment when the three directions of the center line are the arms. As a result, the thickness of the blade is set to t1≧-to, as shown in Figure 5 of the expanded view of the blade, where the thickness on the inlet side is tl and the thickness on the exit side is to. -ru. These airfoils are formed by having the front side of the blade hydrodynamically defined and the back side bulging.

以上の結果、一枚翼羽根車ポンプの羽根車の釣合は静的
にポンプ軸軸心並びにポンプ軸に直交する軸に関する釣
合を翼の厚さで加減することＫよル従来例のようにおも
りを設けたシすることが不要となり、その結果羽根車の
軽量化２！ｌＥ可能となシ、振動を軽減できる。As a result of the above, the balance of the impeller of a single-blade impeller pump is determined by statically adjusting the balance with respect to the pump shaft axis and the axis perpendicular to the pump shaft by adjusting the blade thickness. It is no longer necessary to provide a weight, which results in a lighter impeller 2! It is possible to reduce vibrations.

以上のとおり、本発明は円錐様ポンプケーシングに外周
が円錐様のねじ羽根の翼を有する羽根車を納めたポンプ
において、入口側の翼厚をシヱラウド側と根本側を同一
厚さとし翼のハブへの取付角を従来例よ）も傾けて且つ
入口側と出口側の取付角を異にするよ５ＫＬ、たからボ
ンオｈ　朱ｉ プ効率は増大し、同一吐出し量に対するｍは増大し、ポ
ンプ容量を同一とするとポンプを小さくできる。As described above, the present invention provides a pump in which an impeller having threaded blades with a conical outer circumference is housed in a conical pump casing, in which the thickness of the blades on the inlet side is the same on the shield side and the base side, and the blades are connected to the hub of the blade. By tilting the mounting angle (compared to the conventional example) and making the mounting angles on the inlet and outlet sides different, the pump efficiency will increase, m for the same discharge amount will increase, and the pump capacity will increase. If the values are the same, the pump can be made smaller.

羽根車の釣合をポンプ軸軸心とポンプ軸軸心Ｋ［角な軸
に対する静的釣合と翼の厚さを変化させて保つようにし
たから、羽根車は軽量化でき、振動も軽減できる。The balance of the impeller is maintained between the pump shaft center and the pump shaft center K [static balance with respect to the square shaft and by changing the thickness of the blades, so the impeller can be made lighter and vibrations are reduced. can.

そこでこの種ポンプｆｌＣ＞１４で従来のようにポンプ
完成后に振動を避けるために回転数を変化させることを
予定してベルト駆動を行うように設ける必要もない。以
上のポンプ効率の向上と釣合の精度向上によシ一枚羽根
車ポンプを小原軽量化できる。Therefore, in this type of pump flC>14, there is no need to provide belt drive with the intention of changing the rotational speed to avoid vibrations after the pump is completed, as is the case in the prior art. By improving the pump efficiency and balancing accuracy as described above, it is possible to reduce the weight of the single impeller pump.

【図面の簡単な説明】[Brief explanation of the drawing]

第１図は本発明の実施例の縦断面図、第Ｊ図は第１図の
一部拡大正間図、第３図は第１図の一部正ｗＷＪ、第＃
図は翼の展開図、第３図は第７図の作用の説明図、第４
図は従来例の作用を説明する縦断面略図、第７図は第１
図の一部拡大正ｍ＊、第を図、第を図は本発明の翼形を
示すｒＩｔｉ面であって、第１ＷＪは正面図、第デ図は
縦断面図、第１Ｏ図は従来例の翼形の縦断面図１、第１
１図はポンプ性能の比較線図、第１−図、第ｉ、ｙ図は
羽根車の釣合方法を示すための図画であって第１コ図は
正面図、第７３図は縦断面図である。 ｌ・・羽根車　−・・翼　３・・中心−３′・・ポンプ
主軸　参・・ポングクーシタグ　ｊ・・翼端　６・・吸
込口　７・・吐出ケーシング　ｔ・・円錐様ハブ　デ・
・境界ＩＩＩ　　１０・・放射線　１／・・外周　／コ
・・交点　／３・・裏側　ム／、　）’、　Ｏ’、　Ｄ
’・・微小部分０．０′・・軸心。 第１図 第２図 第３図 第５図 第６図 人 第７ｓFIG. 1 is a vertical sectional view of an embodiment of the present invention, FIG. J is a partially enlarged front view of FIG. 1, and FIG. 3 is a partially enlarged front view of FIG.
The figure is a developed view of the wing, Figure 3 is an explanatory diagram of the action of Figure 7, and Figure 4 is an explanatory diagram of the action of Figure 7.
The figure is a schematic vertical cross-sectional view explaining the operation of the conventional example, and Figure 7 is the first
Partially enlarged regular m* of the figure, Fig. 1 and Fig. 1 are rIti planes showing the airfoil of the present invention, No. 1 WJ is a front view, No. D is a longitudinal sectional view, and No. 1 O is a conventional example. Longitudinal cross-sectional view of the airfoil 1, 1st
Figure 1 is a comparison diagram of pump performance, Figures 1-1, i, and y are diagrams to show how to balance the impeller, and Figure 1 is a front view, and Figure 73 is a longitudinal cross-sectional view. It is. l.. Impeller -.. Blade 3.. Center - 3'.. Pump main shaft.. J.. Blade tip 6.. Suction port 7.. Discharge casing t.. Conical hub De.
・Boundary III 10...Radiation 1/...Outer periphery /K...Intersection /3...Backside Mu/, )', O', D
'...Minute part 0.0'...Axis center. Figure 1 Figure 2 Figure 3 Figure 5 Figure 6 Person 7s

Claims (1)

【特許請求の範囲】[Claims] ｌ　吸込口と吐出ケーシング間が円錐４１１回転面をな
したポンプケーシングに、外周回転面がポンプケーシン
グの円錐様回転ｌ１ｆＫｌｌｉ間少く接近する円錐様を
なしたねじ羽根の翼を円錐様ハブに形成した羽根車をケ
ーシング内にて回転可能に支持した一枚翼羽根車ポンプ
におｉで、翼の厚さが羽根車回転中心を直交してとおる
電線上に存在する翼の部分が回転中心に対して等し一モ
ーメントを持つように翼厚を変え石と共に、羽根車の支
持部をとお夛回転中心Ｋ［交する軸に対する軸方向距離
をアーふとする前記翼の部分のモーメントの合計が零と
なるように翼厚を変化させてなる一枚翼羽根車ポンプ。l On a pump casing with a conical 411 rotating surface between the suction port and the discharge casing, a conical hub is formed with a conical screw blade whose outer circumferential rotating surface approaches the pump casing a little during the conical rotation l1fKlli. In a single-blade impeller pump in which the impeller is rotatably supported within the casing, the thickness of the blade is such that the part of the blade that is on the electric wire passing perpendicularly to the center of rotation of the impeller is relative to the center of rotation. The thickness of the blades is changed so that the blades have an equal moment, and the support part of the impeller is attached to the center of rotation K. A single-blade impeller pump with varying blade thickness.