JPS61185699A - Centrifugal pump - Google Patents

Centrifugal pump

Info

Publication number
JPS61185699A
JPS61185699A JP60024311A JP2431185A JPS61185699A JP S61185699 A JPS61185699 A JP S61185699A JP 60024311 A JP60024311 A JP 60024311A JP 2431185 A JP2431185 A JP 2431185A JP S61185699 A JPS61185699 A JP S61185699A
Authority
JP
Japan
Prior art keywords
impeller
suction
centrifugal pump
suction port
side 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
Application number
JP60024311A
Other languages
Japanese (ja)
Inventor
Sumio Sudo
須藤 純男
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Ltd
Original Assignee
Hitachi Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Hitachi Ltd filed Critical Hitachi Ltd
Priority to JP60024311A priority Critical patent/JPS61185699A/en
Publication of JPS61185699A publication Critical patent/JPS61185699A/en
Pending legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04DNON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00Details, component parts, or accessories
    • F04D29/08Sealings
    • F04D29/16Sealings between pressure and suction sides
    • F04D29/165Sealings between pressure and suction sides especially adapted for liquid pumps
    • F04D29/167Sealings between pressure and suction sides especially adapted for liquid pumps of a centrifugal flow wheel

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

PURPOSE:To reduce the disturbance of main flow by forming a concaved part onto the surface of a casing wearing ring opposed to the suction-side edge surface of the side plate of a vane wheel. CONSTITUTION:Outside the suction port 3b side of the side plate 3a of a vane wheel 4 in a casing 4, a casing wearing ring 6 is fixed onto the casing 4. The passage 10 between the leak-side opened port (a) of a water sealing gap (c) and an effluence port (b) for the leak fluid into a suction passage 1 is formed with the edge surface 3c on the suction port 3b side of the side plate 3a and the surface 6a of the casing wearing ring 6 opposed to the edge surface 3c, and a concaved part 6b is formed in the intermediate part of the surface 6a. Therefore, the speed of the leak fluid is markedly decelerated, and the disturbance of main flow can be reduced markedly.

Description

【発明の詳細な説明】 〔産業上の利用分野〕 この発明は、タービンポンプ、うず巻ポンプ・斜流ポン
プ等の遠心ポンプに係り、特にポンプの吸込性能を向上
させた遠心ポンプに関する。
DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to centrifugal pumps such as turbine pumps, centrifugal pumps, mixed flow pumps, etc., and particularly relates to a centrifugal pump with improved suction performance.

〔健米の技術〕[Kenmai technology]

従来の遠心ポンプは、第4図に示すように、吸込流路1
から吸込まれた液体を、回転軸2と一体的に回転する羽
根i3により昇圧し、ケーシング4内に形成されたうす
室5内に吐出して高圧液体にし、揚液するものである。
A conventional centrifugal pump has a suction channel 1 as shown in FIG.
The pressure of the liquid sucked in from the rotary shaft 2 is increased by a blade i3 that rotates integrally with the rotary shaft 2, and the liquid is discharged into a thin chamber 5 formed in a casing 4 to become a high-pressure liquid and pumped.

このうす室5内の高圧液体の一部は、羽根車3の側板3
aと、該側板3aに対[口」シてケーシング4に配置さ
れたケージ/グラニアリングリング6間の封水隙間C全
通り、高速のジェット流Jとなって吸込流路1内に漏洩
している。このジェット流Jは、吸込流路1より羽根車
3へ向う主流Mの流れに逆う方向に流れているので、主
流Mの流れを乱し、ポンプの吸込性能全低下させる要因
となっていた。またジェット流Jfl、羽根車3の側板
3a内面に沿って流れる主流Mtさえぎって流れるため
、側板3aに沿う境界層を著しく発達させ、境界層のは
くり等の現象が発生し、ポンプ効率低下の要因となって
いた。
A part of the high pressure liquid in this thin chamber 5 is transferred to the side plate 3 of the impeller 3.
a, and the cage/grania ring 6 disposed in the casing 4 with its mouth facing the side plate 3a. ing. Since this jet stream J flows in the opposite direction to the flow of the main stream M from the suction channel 1 toward the impeller 3, it disturbs the flow of the main stream M and becomes a factor that completely reduces the suction performance of the pump. . In addition, since the jet flow Jfl intercepts the main flow Mt flowing along the inner surface of the side plate 3a of the impeller 3, the boundary layer along the side plate 3a develops significantly, and phenomena such as boundary layer peeling occur, resulting in a decrease in pump efficiency. This was a contributing factor.

以上はいずれも封水隙間Cがらの漏洩液体が非常に高速
のジェット流Jでらり、またこのジェット流、■と主流
Mとの流れ方向が大きく(約360°)異なっているこ
とに起因している。
All of the above is due to the fact that the liquid leaking from the sealing gap C flows into a very high-speed jet stream J, and that the flow directions of this jet stream (■) and the mainstream M are greatly different (approximately 360°). are doing.

第5図は、この筏の遠心ポンプの他の従来例を示したも
ので、封水隙間Cからの漏洩液体は、ジェット流Jとな
って側板3aの1敗退流路1側端面3bとそれに対向す
るケーシングウェアリングリング6の面との間を通って
吸込流路1に主fiMとほぼ直交して流出する。従って
、この場合も第4図に示したものと同様、主流Mの流れ
を乱し、ポンプ性能に株々の悪影響を与えていた。
Fig. 5 shows another conventional example of the centrifugal pump for this raft, in which the liquid leaking from the water sealing gap C becomes a jet stream J and reaches the side end face 3b of the 1st retreat channel 1 of the side plate 3a. It flows out into the suction flow path 1 almost perpendicularly to the main fiM through between the opposing surfaces of the casing wear ring 6. Therefore, in this case as well, as in the case shown in FIG. 4, the flow of the main stream M was disturbed and the pump performance was adversely affected.

以上のような問題点を解決するために、第6図に示すよ
うに、封水隙間Cからの高速ジェット流Jを、吸込流路
】より羽根車3へ吸込まれる主流Mの方向に案内するポ
ンプ軸心と同心状の吸込リング8を設けた遠心ポンプが
、特公昭5〇−8202号公報に開示されている。該遠
心ポンプによれば、高速ジェット流Jが主流Mの流れを
乱すことなく羽根車3に吸込まれるので、第4図および
第5図に示した従来の遠心ポンプより吸込性能が高くな
る。
In order to solve the above problems, as shown in FIG. A centrifugal pump provided with a suction ring 8 concentric with the pump axis is disclosed in Japanese Patent Publication No. 50-8202. According to the centrifugal pump, the high-speed jet flow J is sucked into the impeller 3 without disturbing the flow of the main stream M, so that the suction performance is higher than that of the conventional centrifugal pumps shown in FIGS. 4 and 5.

〔発明が解決しよりとする問題点〕[Problems that the invention is supposed to solve]

しかしながら、上記特公昭50−8202号公報に開示
された遠心ポンプでは、吸込リング8をケーシングウェ
アリングリング6とは別に設ける必要があり、ポンプの
製作、組立および分解の各工数が増大し、必然的にコス
ト高になるといり問題があった。また吸込リング8の内
径D11は、羽根車3の目玉径り、より小さくなるため
、吸込リング8部で主fiMの流路断面積が減少し、主
流Mの流速が速くなり、この結果、特にポンプを正規流
量から大流量側で運転する場合、吸込リング8がないも
のに比べ吸込性能およびポンプ効率が低下するという問
題があった。
However, in the centrifugal pump disclosed in Japanese Patent Publication No. 50-8202, it is necessary to provide the suction ring 8 separately from the casing wear ring 6, which increases the number of man-hours for manufacturing, assembling, and disassembling the pump. However, there was a problem in that the cost was high. In addition, the inner diameter D11 of the suction ring 8 becomes smaller than the eye diameter of the impeller 3, so the flow passage cross-sectional area of the main fiM decreases in the suction ring 8 section, and the flow velocity of the main flow M becomes faster. When the pump is operated from the normal flow rate to the large flow rate side, there is a problem in that the suction performance and pump efficiency are lower than those without the suction ring 8.

この発明は、上記事情に鑑みてなされたもので、羽根車
の吸込口側における主流の流路断面積を減少させること
なく、封水隙間からの漏洩液体により羽根車へ吸込まれ
る主流の流れが乱されるのを軽減するようKした遠心ポ
ンプを提供することを目的とするものである。
This invention was made in view of the above-mentioned circumstances, and the main flow that is sucked into the impeller by leaking liquid from the sealing gap without reducing the cross-sectional area of the main flow passage on the suction port side of the impeller. It is an object of the present invention to provide a centrifugal pump that is designed to reduce disturbance of the air flow.

〔問題点?解決するための手段〕〔problem? Means to solve]

かかる目的達成のため、本発明は、羽根車側板の吸込口
側外周面と、それに対向するケーシングウェアリングリ
ングの内面との間に封水隙間を有する遠心ポンプにおい
て、前記側板の吸込口側端面に対向する前記り゛−77
グウエアリングリングの面に凹部を形成したものである
To achieve such an object, the present invention provides a centrifugal pump having a water-sealing gap between the outer circumferential surface of an impeller side plate on the suction port side and the inner surface of a casing wear ring opposing thereto, wherein the end surface of the side plate on the suction port side 77
A concave portion is formed on the surface of the wear ring.

〔作用〕[Effect]

上述の構成によれば、封水隙間を介して羽根車の吸込口
側に漏洩する液体のジェット流は、凹部によυ速度エネ
ルギが消費され減速された後に吸込流路内に流出する。
According to the above configuration, the jet flow of liquid leaking to the suction port side of the impeller through the water sealing gap is decelerated by consuming υ velocity energy by the recess, and then flows out into the suction flow path.

従ってジェット流による主流の流れの乱れが軽減する。Therefore, turbulence in the mainstream flow caused by the jet flow is reduced.

〔実施例〕〔Example〕

以下、本発明を図面に示す実施例に基づいて説明する。 Hereinafter, the present invention will be explained based on embodiments shown in the drawings.

第1図は、両吸込遠心ポンプの羽根車吸込口近傍金示す
部分断面−であり、同図において、第4図に示すものと
同一の部品には同一符号を付して説明する。
FIG. 1 is a partial cross-section showing the vicinity of the impeller suction port of a dual-suction centrifugal pump, and in the same figure, the same parts as those shown in FIG. 4 will be described with the same reference numerals.

ケーシング4内には、回転軸2により回転駆動される羽
根車3が収容されており、該羽根車3の側板3aの吸込
口3b側外方には、ケーシングウェアリングリング6が
ケーシング4に固定されて配置されている。この側板3
aの吸込口3b側外周面と、それに対向するケーシング
ウェアリングリング6の内面との隙間Cは、ここで封水
作用を行なわせるため可及的に僅少な環状の封水隙間と
なっている。この封水隙間Cの漏出側開口部aと、漏洩
液体が吸込流路1に流出する流出口すとの間の通路10
は、側板3aの吸込口3b側端面3Cと該端面3Cに対
向するケーシングウェアリングリング6のi5aで形成
されている。面6aの中間部には、−円弧状などの曲線
からなる断面形状をポンプ軸心(Y−Y軸、第4図参照
)全中心として回転させて形成した凹部6bが設けられ
ている。
An impeller 3 that is rotationally driven by the rotating shaft 2 is housed in the casing 4, and a casing wear ring 6 is fixed to the casing 4 on the outside of the side plate 3a of the impeller 3 on the side of the suction port 3b. has been placed. This side plate 3
The gap C between the outer circumferential surface on the side of the suction port 3b of a and the inner surface of the casing wear ring 6 facing it is an annular water-sealing gap as small as possible in order to perform the water-sealing action here. . A passage 10 between the leakage side opening a of this sealing gap C and the outlet through which the leaked liquid flows out into the suction channel 1
is formed by an end surface 3C of the side plate 3a on the side of the suction port 3b and an i5a of the casing wear ring 6 facing the end surface 3C. A recess 6b is provided in the middle of the surface 6a, which is formed by rotating a cross-sectional shape of a curve such as a -circular arc around the pump axis (Y-Y axis, see FIG. 4).

つぎに、上記本発明の実施例の動作を第4図をも参照に
して説明する。
Next, the operation of the above embodiment of the present invention will be explained with reference to FIG.

回転軸2により羽根車3が回転すると、液体は左右の吸
込流路1(第1図においては右側のみを示す)より羽根
車3の吸込口3bへ吸込まれる。
When the impeller 3 is rotated by the rotating shaft 2, liquid is sucked into the suction port 3b of the impeller 3 through the left and right suction channels 1 (only the right side is shown in FIG. 1).

この液体を羽根車3により昇圧した後、ケーシング4内
に形成されたうす呈5内に吐出し、高圧液体にして揚液
する。
After this liquid is pressurized by the impeller 3, it is discharged into a thin plate 5 formed in the casing 4, and the liquid is made into a high-pressure liquid and pumped.

さて、うす室5内の高圧液体の一部は、封水隙間Cの流
出側開口部aよシ高速ジェット流Jとなって流出し、通
路10内に流入する。このジェット流Jは、凹部6bと
側板3aの端面3Cとにより形成された空間部6C内で
、矢印Aの方向に旋回する旋回流となる。すると、空間
部6Cの周囲の面との摩擦損失や衝突損失などにより、
ジェット流Jのもつ速度エネルギが消費され、ジェット
流Jの流速は減少し、ジェット流Jは低速の流れとなっ
て流出口すから吸込流路1内に流出する。
Now, a part of the high-pressure liquid in the thin chamber 5 flows out as a high-speed jet flow J through the outflow side opening a of the water sealing gap C, and flows into the passage 10. This jet flow J becomes a swirling flow that swirls in the direction of arrow A within a space 6C formed by the recess 6b and the end surface 3C of the side plate 3a. Then, due to friction loss and collision loss with the surrounding surfaces of the space 6C,
The velocity energy of the jet stream J is consumed, the flow velocity of the jet stream J decreases, and the jet stream J becomes a low-velocity flow and flows out from the outlet into the suction channel 1.

従って、第4図および第5図に示す従来の遠心ポンプの
ように、封水隙間Cからの高速ジェット流Jが、そのま
ま吸込流路1に流出する場合に比較してジェット流Jの
流速が低速になっているので、吸込流路1より羽根車3
へ向う主流Mの乱れが大幅に軽減される。
Therefore, as in the conventional centrifugal pump shown in FIGS. 4 and 5, the flow velocity of the jet flow J is lower than that in the case where the high-speed jet flow J from the sealing gap C directly flows into the suction channel 1. Since the speed is low, the impeller 3 is lower than the suction flow path 1.
The turbulence of the main flow M toward the main stream M is significantly reduced.

また主流Mの乱れを軽減させる手段として、第6図に示
す如き、羽根車吸込口3b部で主流Mの流路断面積を減
少させる吸込リング26を用いていないので、大流量運
転時にも良好な吸込性能が得られる。
Furthermore, as a means for reducing the turbulence of the main stream M, the suction ring 26 that reduces the flow path area of the main stream M at the impeller suction port 3b is not used as shown in FIG. Achieving excellent suction performance.

なお第1図においては、側板3aの吸込口側端面3Cと
対向するケーシングウェアリングリング6の面6aに円
弧状からなる凹部6bi設けているが、この凹部6bの
形状は、円弧状に限定されることなく、例えば第2図に
示すように多角形状にしてもよい。また同図に示すよう
に、凹部6bに対向して側板3aの吸込口側端面3cに
も同様凹部3d′ft、設けると相乗的効果がるる。
In FIG. 1, an arc-shaped recess 6bi is provided on the surface 6a of the casing wear ring 6 facing the suction port side end surface 3C of the side plate 3a, but the shape of this recess 6b is limited to an arc. For example, as shown in FIG. 2, the shape may be polygonal. Further, as shown in the figure, if a similar recess 3d'ft is provided on the suction port side end surface 3c of the side plate 3a opposite to the recess 6b, a synergistic effect can be obtained.

第3図は本発明の他の実施例を示したものであり、羽根
車側板3aの吸込口3b側の内径DIを羽根車3の目玉
径り、より太きくシ、羽根車吸込部内壁面3di直径D
+ よりD■に減少するテーパ状となし、またゲージン
グウェアリングリング6の内径fDw+、凹部6bの最
小径をDvlとするとき、Dvt≧D a + Dvs
≦D+ として、空間部6Cから事根車吸込口3b側へ
の漏洩液体が、テーパ状に形成された内壁面3dに沿っ
て羽根車3の吸込口3bへ向って吸込まれるようになっ
ている。これによって、封水隙間Cよりジェット流Jと
なって流出する漏洩液体を凹部6bで旋回させ、ジェッ
ト流Jの速度エネルギを減少させるのみでなく、さらに
この低速となった漏液成体の流れ方向を内壁面3dによ
って、羽根車3に吸込まれる主fiMの流れ方向に変え
ることにより、主流Mの乱れがさらに軽減される。
FIG. 3 shows another embodiment of the present invention, in which the inner diameter DI of the impeller side plate 3a on the suction port 3b side is the diameter of the eye of the impeller 3, the inner diameter DI of the impeller 3 is made thicker, and the inner diameter DI of the impeller suction part inner wall surface 3DI is the diameter of the eye of the impeller 3. Diameter D
When the inner diameter of the gauging wear ring 6 is fDw+ and the minimum diameter of the recess 6b is Dvl, Dvt≧D a + Dvs.
≦D+, the leaked liquid from the space 6C toward the root wheel suction port 3b is sucked toward the impeller 3 suction port 3b along the tapered inner wall surface 3d. There is. As a result, the leaked liquid flowing out as a jet stream J from the sealing gap C is swirled in the recess 6b, and not only the velocity energy of the jet stream J is reduced, but also the flow direction of the leaked liquid substance that has become low velocity By changing the flow direction of the main fiM sucked into the impeller 3 by the inner wall surface 3d, the turbulence of the main flow M is further reduced.

また直径D v I≧D、となるように設定されている
ので、羽根車吸込口3b部で主KMの流路断面績が絞ら
れることがないため、大流量運転時にも良好な吸込性能
を得ることができる。
In addition, since the diameter is set so that D v I≧D, the flow path cross-section of the main KM is not restricted at the impeller suction port 3b, so good suction performance can be achieved even during high flow rate operation. Obtainable.

なお本発明は、両吸込遠心ポンプのみでなく、片吸込遠
心ポンプ、羽根車の吐出側にディフューザを有する遠心
ポンプ等、吸込側の側板を有する羽根車(クローズ羽根
車)を用いる遠心ポンプ全般に適用されるものである。
The present invention is applicable not only to double-suction centrifugal pumps, but also to centrifugal pumps in general that use an impeller with a side plate on the suction side (closed impeller), such as single-suction centrifugal pumps, centrifugal pumps with a diffuser on the discharge side of the impeller, etc. applicable.

〔発明の効果〕〔Effect of the invention〕

上述のとおり、本発明によれば、封水隙間からジェット
流となって流出する漏洩液体は、大幅に減速されるので
、主流の乱れを大幅に軽減させることができ、ポンプの
吸込性能を向上させることができる。またケーシングウ
ェアリングリングに凹部を設けるだけでよいので、ポン
プの製造、組立、分解が容易となり、コストを低減させ
ることができる。
As described above, according to the present invention, the leakage liquid flowing out as a jet stream from the water sealing gap is significantly decelerated, so that the turbulence of the mainstream can be significantly reduced, and the suction performance of the pump is improved. can be done. Further, since it is only necessary to provide a recess in the casing wear ring, manufacturing, assembly, and disassembly of the pump are facilitated, and costs can be reduced.

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

第1図から第3図は本発明の実施例に係り、第1図は遠
心ポンプの羽根車近傍を示した部分縦断面図、第20は
第1図に示すものの他の実施例の部分縦断面図、第3図
は第1図に示すもののさらに他の実施例の部分縦断面図
、第4図は従来例の遠心ポンプの一部を省略して示した
概略縦断面図、第5図は他の従来例の羽根車近傍の部分
縦断面図、第6図はさらに他の従来例の遠心ポンプの一
部を省略して示した概略縦断面■である。 3・・・羽根車、3a・・・側板、3b・・・吸込口、
3C・・・端面、6・・・ケーシングウェアリングリン
グ、6b¥:J  1  図 v Z 図 第  3  図 冨 4 図
1 to 3 relate to embodiments of the present invention, FIG. 1 is a partial vertical cross-sectional view showing the vicinity of the impeller of a centrifugal pump, and FIG. 20 is a partial vertical cross-sectional view of another embodiment of the invention shown in FIG. 3 is a partial vertical cross-sectional view of still another embodiment of the one shown in FIG. 1; FIG. 4 is a schematic vertical cross-sectional view of a conventional centrifugal pump with some parts omitted; and FIG. 6 is a partial vertical cross-sectional view of the vicinity of an impeller of another conventional example, and FIG. 6 is a schematic vertical cross-sectional view (2) of another conventional centrifugal pump with some parts omitted. 3... Impeller, 3a... Side plate, 3b... Suction port,
3C... End face, 6... Casing wear ring, 6b ¥: J 1 Fig. v Z Fig. 3 Fig. 4 Fig.

Claims (1)

【特許請求の範囲】 1、羽根車側板の吸込口側外周面と、それに対向するケ
ーシングウェアリングリングの内面との間に封水隙間を
有する遠心ポンプにおいて、前記側板の吸込口側端面に
対向する前記ケーシングウェアリングリングの面に凹部
を形成したことを特徴とする遠心ポンプ。 2、前記凹部を、円弧状などの曲線からなる断面形状を
ポンプ軸心を中心として回転させて形成した凹面状とし
たことを特徴とする特許請求の範囲第1項に記載の遠心
ポンプ。 3、前記凹部を、多角形からなる断面形状をポンプ軸心
を中心として回転させて形成した凹面状としたことを特
徴とする特許請求の範囲第1項に記載の遠心ポンプ。 4、前記羽根車側板の吸込口側端面の内径D_1を羽根
車目玉径D_■より大きくし、羽根車吸込部内壁面を直
径D_1よりD_■に減少するテーパ状となし、また前
記ケーシングウェアリングリングの内径をD_w_1、
凹部の最小径をD_w_1とするとき、D_w_1≧D
_■、D_w_1≦D_1とし、前記羽根車側板の吸込
口側端面とそれに対向する前記凹部との間に形成された
空間部から前記羽根車吸込口側への漏洩液が前記羽根車
吸込部内壁面に沿つて前記羽根車の吸込口に吸込まれる
ように構成したことを特徴とする特許請求の範囲第1項
に記載の遠心ポンプ。
[Claims] 1. In a centrifugal pump having a water-sealing gap between the outer circumferential surface of the impeller side plate on the suction port side and the inner surface of the casing wear ring opposing thereto, A centrifugal pump characterized in that a recess is formed in a surface of the casing wear ring. 2. The centrifugal pump according to claim 1, wherein the recessed portion has a concave shape formed by rotating a cross-sectional shape of a curved line such as an arc around the pump axis. 3. The centrifugal pump according to claim 1, wherein the recessed portion has a concave shape formed by rotating a polygonal cross-sectional shape around the pump axis. 4. The inner diameter D_1 of the end surface on the suction port side of the impeller side plate is made larger than the impeller eye diameter D_■, and the inner wall surface of the impeller suction part is tapered to decrease from the diameter D_1 to D_■, and the casing wear ring. The inner diameter of is D_w_1,
When the minimum diameter of the recess is D_w_1, D_w_1≧D
_■, D_w_1≦D_1, and the liquid leaking from the space formed between the end face of the impeller side plate on the suction port side and the recess facing thereto toward the impeller suction port is absorbed by the inner wall surface of the impeller suction part. 2. The centrifugal pump according to claim 1, wherein the centrifugal pump is configured to be sucked into the suction port of the impeller along the direction of the impeller.
JP60024311A 1985-02-13 1985-02-13 Centrifugal pump Pending JPS61185699A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP60024311A JPS61185699A (en) 1985-02-13 1985-02-13 Centrifugal pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP60024311A JPS61185699A (en) 1985-02-13 1985-02-13 Centrifugal pump

Publications (1)

Publication Number Publication Date
JPS61185699A true JPS61185699A (en) 1986-08-19

Family

ID=12134629

Family Applications (1)

Application Number Title Priority Date Filing Date
JP60024311A Pending JPS61185699A (en) 1985-02-13 1985-02-13 Centrifugal pump

Country Status (1)

Country Link
JP (1) JPS61185699A (en)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06147195A (en) * 1992-10-30 1994-05-27 Ishikawajima Harima Heavy Ind Co Ltd Compressor housing of turbo charger
JPH0914194A (en) * 1995-06-29 1997-01-14 Daewoo Electronics Co Ltd Circulating pump
JP2000074410A (en) * 1998-09-03 2000-03-14 Daikin Ind Ltd Double suction centrifugal fan and air supplying apparatus provided therewith
JP2013189916A (en) * 2012-03-13 2013-09-26 Mitsubishi Heavy Ind Ltd Pump, and mechanism for suppressing interference of pump leakage flow
JP2014084803A (en) * 2012-10-24 2014-05-12 Mitsubishi Heavy Ind Ltd Centrifugal fluid machine
JP2014167268A (en) * 2013-02-28 2014-09-11 Mitsubishi Heavy Ind Ltd Multistage centrifugal fluid machine
JP2020197132A (en) * 2019-05-31 2020-12-10 三菱重工業株式会社 Rotary machine

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS55128695A (en) * 1979-03-26 1980-10-04 Hitachi Ltd Centrifugal pump

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS55128695A (en) * 1979-03-26 1980-10-04 Hitachi Ltd Centrifugal pump

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06147195A (en) * 1992-10-30 1994-05-27 Ishikawajima Harima Heavy Ind Co Ltd Compressor housing of turbo charger
JPH0914194A (en) * 1995-06-29 1997-01-14 Daewoo Electronics Co Ltd Circulating pump
JP2000074410A (en) * 1998-09-03 2000-03-14 Daikin Ind Ltd Double suction centrifugal fan and air supplying apparatus provided therewith
JP2013189916A (en) * 2012-03-13 2013-09-26 Mitsubishi Heavy Ind Ltd Pump, and mechanism for suppressing interference of pump leakage flow
JP2014084803A (en) * 2012-10-24 2014-05-12 Mitsubishi Heavy Ind Ltd Centrifugal fluid machine
JP2014167268A (en) * 2013-02-28 2014-09-11 Mitsubishi Heavy Ind Ltd Multistage centrifugal fluid machine
JP2020197132A (en) * 2019-05-31 2020-12-10 三菱重工業株式会社 Rotary machine

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