JPS5879698A - Impeller structure for centrifugal pump - Google Patents
Impeller structure for centrifugal pumpInfo
- Publication number
- JPS5879698A JPS5879698A JP17653581A JP17653581A JPS5879698A JP S5879698 A JPS5879698 A JP S5879698A JP 17653581 A JP17653581 A JP 17653581A JP 17653581 A JP17653581 A JP 17653581A JP S5879698 A JPS5879698 A JP S5879698A
- Authority
- JP
- Japan
- Prior art keywords
- impeller
- pump
- main plate
- blade
- centrifugal pump
- 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
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
- F04D29/18—Rotors
- F04D29/22—Rotors specially for centrifugal pumps
- F04D29/2205—Conventional flow pattern
- F04D29/2216—Shape, geometry
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Geometry (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】
本発明は遠心ポンプ、主として渦巻ポンプの羽根車構造
に関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an impeller structure for a centrifugal pump, primarily a centrifugal pump.
従来よりの渦巻ポンプの一例を要部縦断面図で第１図に
示す。第１図において１＃′ｉ羽根車、２は側板（前面
シュラウド）で、２１はこの羽根車のマウス部を示す。An example of a conventional centrifugal pump is shown in FIG. 1 as a vertical sectional view of the main part. In FIG. 1, 1#'i impeller, 2 is a side plate (front shroud), and 21 is a mouth portion of this impeller.
３は主板（後面シュラウド）、６は羽根、１０は回転軸
、５はケーシング本体、４はケーシングであって、羽根
車のマウス部２′との対向面にはマウスリング１１が嵌
装しである。羽根車１はその主板３の中心の個所で、ケ
ーシング本体５、ケーシング４で形成されるポンプ室内
で回転軸１０に回転自在に支承されている。主板３には
、液の流入の中心部を除き主板３０周縁までに、一定曲
率で同方向に゛彎曲された複数の羽根６が設けてあり、
羽根６の他の側縁には、その全体をおおう環状の円板の
側板２が取付けられ、羽根車１０室並びに液流入口（Ｉ
Ｉ板中央）及び液排出口（主板、側板、羽根の周縁部）
が形成されている。3 is a main plate (rear shroud), 6 is a blade, 10 is a rotating shaft, 5 is a casing body, 4 is a casing, and a mouth ring 11 is fitted on the surface facing the mouth portion 2' of the impeller. be. The impeller 1 is rotatably supported on a rotating shaft 10 at the center of its main plate 3 within a pump chamber formed by a casing body 5 and a casing 4. The main plate 3 is provided with a plurality of blades 6 which are curved in the same direction at a constant curvature up to the periphery of the main plate 30 except for the center part where the liquid flows.
A side plate 2 in the form of an annular disk is attached to the other side edge of the blade 6 to cover the entire blade, and is connected to the impeller 10 chamber and the liquid inlet (I).
center of I plate) and liquid outlet (main plate, side plate, periphery of blade)
is formed.
従来より遠心ポンプの効率向上の手段は種々提案されて
いる。ポンプ効率を低下する要因として種々考えられる
が、羽根車の主板及び側板の裏面に働く置体摩擦抵抗に
よる損失（円板摩擦損失という。）が比較的大きな要因
をなし、ポンプ効率を改善する上で大きな障害となって
いる。この円板摩擦損失はポンプの比速度が小さいほど
大となる。比速度１５８のポンプの損失分析をした結果
をＩＡ１表に示す。Conventionally, various means for improving the efficiency of centrifugal pumps have been proposed. Various factors can be considered to reduce pump efficiency, but the loss due to the frictional resistance of the mounting body acting on the back surface of the main plate and side plate of the impeller (referred to as disk friction loss) is a relatively large factor, and it is important to improve pump efficiency. has become a major obstacle. This disc friction loss increases as the specific speed of the pump decreases. The results of a loss analysis for a pump with a specific speed of 158 are shown in Table IA1.
第 １ 表
第１表から明らかなように、このような低比速度ポンプ
においては円板摩擦損失の割合が４８１１１１１Ｃも達
し、ポンプ効率改善の上で大きな問題となっている。従
来よシ円板摩擦損失低減の為に主板及び側板の加工精度
を上けたり、その面を鏡面仕上げしたシ′、さらに塗装
を行うことによシ摩擦抵抗を下げることが試みられてい
るが、これらによる損失低減は僅かである。Table 1 As is clear from Table 1, in such a low specific speed pump, the disc friction loss ratio reaches as high as 4811111C, which is a major problem in improving pump efficiency. Conventionally, in order to reduce disc friction loss, attempts have been made to improve the machining accuracy of the main plate and side plates, and to reduce frictional resistance by mirror-finishing their surfaces and painting them. , the loss reduction caused by these is slight.
本発明の目的は、円板摩擦損失が低減され、ポンプ効率
が改善された遠心ポンプの羽根車構造を提供するにある
。An object of the present invention is to provide an impeller structure for a centrifugal pump in which disk friction loss is reduced and pump efficiency is improved.
本発明の他の目的は円板摩擦損失が低減されると共に、
主板、側板とケーシングとの間隙よりの漏れが抑制され
、ポンプ効率の改善された遠心ポンプの羽根車構造を提
供する（Ｔｏる。Another object of the present invention is to reduce disk friction loss and to
To provide an impeller structure for a centrifugal pump in which leakage from gaps between a main plate, a side plate, and a casing is suppressed and pump efficiency is improved.
本発明による遠心ポンプの羽根車構造は、羽根、主板及
び側板を有する遠心ポンプの羽根車構造において、主板
、側板又は主板及び側板の外径を羽根の外縁径より小と
し、羽根の周縁部の側面を露出しであることを特徴とす
る。In the impeller structure of a centrifugal pump according to the present invention, in the impeller structure of a centrifugal pump having a blade, a main plate, and a side plate, the outer diameter of the main plate, the side plate, or the main plate and the side plate is smaller than the outer diameter of the blade, and the outer diameter of the blade is smaller than the outer diameter of the blade. It is characterized by having exposed sides.
本発明による遠心ポンプの羽根車構造の好ましい一態様
においては、前記羽根の周縁部側面を露出した部分を、
ケーシングに取付けられ５た環状ピースにより僅かな間
隙を保っておおっていることである。In a preferred embodiment of the impeller structure of the centrifugal pump according to the present invention, the exposed peripheral side surface of the blade is
The casing is covered with a small gap by an annular piece attached to the casing.
ここで、遠心ポンプにおいて問題となる円板摩擦モーメ
ントについて説明する。流体で満されている円筒容器内
で円板を回転させた場合、円板両側面の摩擦抵抗に費さ
れる力、即ち円板摩擦モーメン）Ｍは（１７式で与えら
れる。Here, the disk friction moment, which is a problem in centrifugal pumps, will be explained. When a disk is rotated in a cylindrical container filled with fluid, the force exerted by the frictional resistance on both sides of the disk, ie, disk friction moment) M is given by (Equation 17).
””ＣＭ＠Ｐ ” Ｒ”／２ （１）
但し、ＣＭ：摩擦モーメント係数、Ｐ：流体密度、Ｒ：
円板外径、ｍ：円板角速度。""CM@P "R"/2 (1)
However, CM: friction moment coefficient, P: fluid density, R:
Disk outer diameter, m: disk angular velocity.
即ち、ポンプ損失としての円板摩擦損失の大きさは、羽
根車の主板及び側板の外径の５乗に比例する。That is, the magnitude of the disk friction loss as a pump loss is proportional to the fifth power of the outer diameter of the main plate and side plate of the impeller.
本発明によるポンプは羽根車の主板、側板のうちいずれ
か一方、又は両者の外径を羽根の外縁径より小さくしで
あるので、従来のポンプよりも円板摩擦損失を低減させ
ることができる。In the pump according to the present invention, the outer diameter of one or both of the main plate and the side plate of the impeller is smaller than the outer edge diameter of the blade, so that disc friction loss can be reduced more than in conventional pumps.
次に、本発明によるポンプの羽根車構造を実施例の図面
に基づいて説明する。第２図は本発明のポンプの実施例
の第１図の従来のポンプに対応する縦断面図である。第
１図と同一部位は同一符号で示しである。このポンプの
羽根車１人においては、主板！ＩＡ及び側板２人の外径
を羽根６の外縁径より小さくしである。即ち、主板５Ａ
及び側板２人は羽根車１Ａの周縁オで延伸せず、羽根６
の側面が羽根車の周縁部において露出している。このよ
うにこのポンプの主板５Ａ及び側板ハは従来の主板３及
び側板２よシ外径が小さいので、その主板、側板の終端
部において、ケーシング４とケーシング本体５並びに主
板３、側板２との間で発生する円板摩擦損失は少なくな
る。勿論、主板５Ａ又は側板２＾のみの外径を小さくし
て４、その効果は充分に得られる。Next, the impeller structure of a pump according to the present invention will be explained based on drawings of embodiments. FIG. 2 is a longitudinal sectional view of an embodiment of the pump of the present invention, which corresponds to the conventional pump of FIG. The same parts as in FIG. 1 are indicated by the same symbols. In one impeller of this pump, the main plate! The outer diameter of the IA and the two side plates is made smaller than the outer edge diameter of the blade 6. That is, the main plate 5A
And the two side plates do not extend at the peripheral edge of the impeller 1A, and the blade 6
The side surface of the impeller is exposed at the periphery of the impeller. In this way, the main plate 5A and side plate C of this pump have smaller outer diameters than the conventional main plate 3 and side plate 2, so that the casing 4 and the casing body 5 as well as the main plate 3 and side plate 2 are connected at the terminal ends of the main plate and side plate. The disc friction loss that occurs between the two is reduced. Of course, the effect can be sufficiently obtained by reducing the outer diameter of only the main plate 5A or the side plates 2^.
第３図に本発明のポンプの他の実施例を示す。FIG. 3 shows another embodiment of the pump of the present invention.
この実施例においては、羽根車１人の周縁部の羽根Ａの
側面が露出する部は、ケーシング４及びケーシング本体
５内面に設けられた環状ピース７及び８によ多価かな間
１１９を保っておおわれている。In this embodiment, the portion where the side surface of the blade A at the peripheral edge of one impeller is exposed maintains a polygonal gap 119 to the annular pieces 7 and 8 provided on the inner surface of the casing 4 and the casing body 5. It's covered.
環状ピース７及び８はそれぞれケーシング４及びケーシ
ング本体と一体として作成してもよい。The annular pieces 7 and 8 may be made integral with the casing 4 and the casing body, respectively.
この実施例のポンプにおいては、環状ピース７により羽
根車１人や液流出側の高圧液体が主板５Ａ。In the pump of this embodiment, one impeller and the high pressure liquid on the liquid outflow side are connected to the main plate 5A by the annular piece 7.
側板話とケーシングの間を通って漏れることが抑制され
る。Leakage between the side plate and the casing is suppressed.
本発明のポンプの羽根車は以上の如く構成されているの
で、ポンプの円板摩擦損失を低減し、ポンプ効率を改善
することができる。また、更に露出羽根に対向して僅か
な間隙の環状ピースを設けることによって、液の漏れを
抑制しポンプ効率を更に改善することがてきる。Since the impeller of the pump of the present invention is configured as described above, it is possible to reduce disk friction loss of the pump and improve pump efficiency. Furthermore, by providing an annular piece with a small gap opposite the exposed blade, leakage of liquid can be suppressed and pump efficiency can be further improved.
第１図は従来の渦巻ポンプの一例の要部縦断面図、第２
図及び第・３図は本発明の渦巻ポンプのそれぞれ異なる
実施例の第１図に対応する要部縦断面図である。
１．１人・・・羽根車、２．２人・・・側板、５．５Ａ
・・・主板、４・・・ケーシング、５・・・ケーシング
本体、６・・・羽根、７．８・・・環状ピース、９・・
・間隙、１０・・・回転軸。
代理人 弁理士 秋 本 正 実
第３図
第１頁の続き
０発 明 者 森岡吟也
習志野市東習志野七丁目１番１
号株式会社日立製作所習志野工
場内Figure 1 is a vertical sectional view of the main part of an example of a conventional centrifugal pump, Figure 2
3 and 3 are longitudinal sectional views of essential parts corresponding to FIG. 1 of different embodiments of the centrifugal pump of the present invention. 1.1 person...impeller, 2.2 person...side plate, 5.5A
...Main plate, 4...Casing, 5...Casing body, 6...Blade, 7.8...Annular piece, 9...
・Gap, 10...Rotation axis. Agent: Tadashi Akimoto, Patent Attorney (Continued from Figure 3, Page 1) 0 Author: Ginya Morioka 7-1-1 Higashi-Narashino, Narashino City, Narashino Factory, Hitachi, Ltd.
Claims (1)
構造において、主板、側板又は主板及び側板の外径を羽
根の外縁径より小とし、羽根の周縁部の側面を露出して
めることを特徴とする遠心ポンプの羽根車構造。 ２、前記羽根周縁部のＩＩＥＩを、露出している部分は
、ケーシングに取付けられた環状ピースにより僅かな間
隙を保っておおわれている特許請求の範囲第１項記載の
遠心ポンプの羽根車構造。[Claims] 1. In the impeller structure of a centrifugal pump having blades, a main plate, and a side plate, the outer diameter of the main plate, the side plate, or the main plate and the side plate is smaller than the outer diameter of the blade, and the side surface of the peripheral edge of the blade is exposed. The impeller structure of a centrifugal pump is characterized by 2. The impeller structure for a centrifugal pump according to claim 1, wherein the exposed portion of the IIIE of the blade peripheral portion is covered with a small gap by an annular piece attached to the casing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17653581A JPS5879698A (en) | 1981-11-05 | 1981-11-05 | Impeller structure for centrifugal pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17653581A JPS5879698A (en) | 1981-11-05 | 1981-11-05 | Impeller structure for centrifugal pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5879698A true JPS5879698A (en) | 1983-05-13 |
| JPS6151680B2 JPS6151680B2 (en) | 1986-11-10 |
Family
ID=16015299
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17653581A Granted JPS5879698A (en) | 1981-11-05 | 1981-11-05 | Impeller structure for centrifugal pump |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5879698A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104165157A (en) * | 2014-07-25 | 2014-11-26 | 江苏大学 | Axial single-end suction impeller with liquid discharged out of two sides |
| EP4405565A4 (en) * | 2021-09-24 | 2025-08-13 | Services Petroliers Schlumberger | STAGE FOR HIGH VISCOSITY |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3368744A (en) * | 1967-03-08 | 1968-02-13 | Jenn Air Corp | Ventilator fan impeller |
| JPS4719804U (en) * | 1971-01-14 | 1972-11-06 |
-
1981
- 1981-11-05 JP JP17653581A patent/JPS5879698A/en active Granted
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3368744A (en) * | 1967-03-08 | 1968-02-13 | Jenn Air Corp | Ventilator fan impeller |
| JPS4719804U (en) * | 1971-01-14 | 1972-11-06 |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104165157A (en) * | 2014-07-25 | 2014-11-26 | 江苏大学 | Axial single-end suction impeller with liquid discharged out of two sides |
| EP4405565A4 (en) * | 2021-09-24 | 2025-08-13 | Services Petroliers Schlumberger | STAGE FOR HIGH VISCOSITY |
| US12529382B2 (en) | 2021-09-24 | 2026-01-20 | Onesubsea Ip Uk Limited | High viscosity stage |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6151680B2 (en) | 1986-11-10 |
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