JPS61185699A - Centrifugal pump - Google Patents
Centrifugal pumpInfo
- 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
Links
- 238000007789 sealing Methods 0.000 claims abstract description 14
- 239000007788 liquid Substances 0.000 claims description 19
- 230000007423 decrease Effects 0.000 claims description 4
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 abstract description 5
- 239000012530 fluid Substances 0.000 abstract 2
- 230000000694 effects Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 241001069515 Grania <Rhodophyta> Species 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 230000002195 synergetic effect Effects 0.000 description 1
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
- F04D29/08—Sealings
- F04D29/16—Sealings between pressure and suction sides
- F04D29/165—Sealings between pressure and suction sides especially adapted for liquid pumps
- F04D29/167—Sealings 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
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.
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.
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.
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.
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.
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.
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.
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)
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.
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)
| 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)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS55128695A (en) * | 1979-03-26 | 1980-10-04 | Hitachi Ltd | Centrifugal pump |
-
1985
- 1985-02-13 JP JP60024311A patent/JPS61185699A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS55128695A (en) * | 1979-03-26 | 1980-10-04 | Hitachi Ltd | Centrifugal pump |
Cited By (7)
| 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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