JP2003021096A - Low loss centrifugal pump - Google Patents
Low loss centrifugal pumpInfo
- Publication number
- JP2003021096A JP2003021096A JP2001207312A JP2001207312A JP2003021096A JP 2003021096 A JP2003021096 A JP 2003021096A JP 2001207312 A JP2001207312 A JP 2001207312A JP 2001207312 A JP2001207312 A JP 2001207312A JP 2003021096 A JP2003021096 A JP 2003021096A
- Authority
- JP
- Japan
- Prior art keywords
- centrifugal pump
- casing
- impeller
- low
- pressure
- 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
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、円板摩擦による損
失が少なく、低流量で使用しても流体の温度上昇が少な
い低損失遠心ポンプに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a low-loss centrifugal pump which has a small loss due to disc friction and a small temperature rise of fluid even when used at a low flow rate.
【０００２】[0002]
【従来の技術】図３は、ジェットエンジンの燃焼器に燃
料を噴射するための従来の燃料流量制御装置の構成図で
ある。この図において、１は燃料ポンプ、２は計量バル
ブ、３はドレインバルブ、４はノズルであり、燃料ポン
プ１で加圧した液体燃料（ジェット燃料）を、計量バル
ブ２で計量（流量調節）し、ドレインバルブ３を開き、
ノズル４から燃焼器（図示せず）に噴射するようになっ
ている。2. Description of the Related Art FIG. 3 is a block diagram of a conventional fuel flow rate control device for injecting fuel into a combustor of a jet engine. In this figure, 1 is a fuel pump, 2 is a metering valve, 3 is a drain valve, 4 is a nozzle, and liquid fuel (jet fuel) pressurized by the fuel pump 1 is metered (flow rate adjusted) by the metering valve 2. , Open the drain valve 3,
It is designed to inject from a nozzle 4 to a combustor (not shown).
【０００３】また、余分な燃料を燃料ポンプ１の上流側
に戻すためのバイパスバルブ５と、このバイパスバルブ
５を制御して、計量バルブ２の上流側圧力Ｐ1と下流側
圧力Ｐ2の差圧ΔＰを一定に制御する差圧センサーバル
ブ６とを備えている。Further, a bypass valve 5 for returning excess fuel to the upstream side of the fuel pump 1, and a control of the bypass valve 5, the difference between the upstream pressure P 1 and the downstream pressure P 2 of the metering valve 2 is controlled. The differential pressure sensor valve 6 controls the pressure ΔP to be constant.
【０００４】計量バルブ２は、計量スプール２ａとノズ
ルフラッパ２ｂを有し、ノズルフラッパ２ｂを電気的又
は機械的に移動（図で左右に）させることにより、計量
スプール２ａの左端に作用する流体圧が変化し、計量ス
プール２ａを左右に移動させて通過流量を制御する。例
えば、この図でノズルフラッパ２ｂを右に移動させる
と、計量スプール２ａの左端圧力が上昇し、計量スプー
ル２ａが右に移動して流量を絞り、逆にノズルフラッパ
２ｂを左に移動させると、計量スプール２ａの左端圧力
が低下し、計量スプール２ａが左に移動して流量が増加
する。The metering valve 2 has a metering spool 2a and a nozzle flapper 2b. By moving the nozzle flapper 2b electrically or mechanically (left and right in the figure), the fluid pressure acting on the left end of the metering spool 2a is changed. Then, the measuring spool 2a is moved to the left and right to control the passing flow rate. For example, when the nozzle flapper 2b is moved to the right in this figure, the left end pressure of the measuring spool 2a rises, the measuring spool 2a moves to the right and throttles the flow rate, and conversely, when the nozzle flapper 2b is moved to the left, The pressure at the left end of 2a decreases, the metering spool 2a moves to the left, and the flow rate increases.
【０００５】計量バルブ２は、上流側圧力Ｐ1と下流側
圧力Ｐ2の差圧ΔＰを一定に保持することにより、ノズ
ルフラッパ２ｂの変位に通過流量が比例する。そのた
め、差圧センサーバルブ６のスプール６ａをバネ６で図
で左側に付勢し、スプール６ａの左端に上流側圧力
Ｐ1、右端に下流側圧力Ｐ2をそれぞれパイロットライン
７ａ，７ｂで導いている。The metering valve 2 maintains a constant differential pressure ΔP between the upstream pressure P 1 and the downstream pressure P 2 , so that the flow rate of passage is proportional to the displacement of the nozzle flapper 2b. Therefore, the spool 6a of the differential pressure sensor valve 6 is biased to the left side in the drawing by the spring 6, and the upstream pressure P 1 is introduced to the left end of the spool 6a and the downstream pressure P 2 is introduced to the right end of the spool 6a by the pilot lines 7a and 7b, respectively. There is.
【０００６】差圧ΔＰが所定の値より小さくなると、こ
の図でスプール６ａが左に移動し、パイロットライン８
ａから８ｂに高圧（上流側圧力Ｐ1）の燃料が流れ、バ
イパスバルブ５のスプール５ａを右に移動してバイパス
ライン９ｂを閉じ、上流側圧力Ｐ1を高め計量バルブ２
の通過流量を増加させる。When the differential pressure ΔP becomes smaller than a predetermined value, the spool 6a moves to the left in this figure, and the pilot line 8
High-pressure (upstream pressure P 1 ) fuel flows from a to 8b, the spool 5a of the bypass valve 5 is moved to the right to close the bypass line 9b, and the upstream pressure P 1 is increased to increase the metering valve 2
Increase the flow rate of
【０００７】逆に、差圧ΔＰが所定の値より大きくなる
と、この図でスプール６ａが右に移動し、バイパスバル
ブ５のバネ５ｂ側の圧力をパイロットライン８ｂ，８ｃ
を介して燃料ポンプ１の上流側（低圧部）に抜き、バイ
パスバルブ５のスプール５ａを左に移動してバイパスラ
イン９ｂを開き、上流側圧力Ｐ1を下げ計量バルブ２の
通過流量を減少させる。On the contrary, when the differential pressure ΔP becomes larger than a predetermined value, the spool 6a moves to the right in this figure, and the pressure on the spring 5b side of the bypass valve 5 is adjusted to the pilot lines 8b, 8c.
Via the fuel pump 1 to the upstream side (low pressure portion), the spool 5a of the bypass valve 5 is moved to the left to open the bypass line 9b, and the upstream pressure P 1 is lowered to reduce the flow rate of the metering valve 2. .
【０００８】上述した構成により、差圧センサーバルブ
６により上流側圧力Ｐ1と下流側圧力Ｐ2の差圧ΔＰを常
に一定に保持し、ノズルフラッパ２ｂの変位に比例した
燃料流量をノズル４から噴射することができるようにな
っている。With the above-described structure, the differential pressure sensor valve 6 always maintains the differential pressure ΔP between the upstream pressure P 1 and the downstream pressure P 2 constant, and the fuel flow rate proportional to the displacement of the nozzle flapper 2b is injected from the nozzle 4. You can do it.
【０００９】[0009]
【発明が解決しようとする課題】上述した航空用エンジ
ンの燃料流量制御装置では、大流量を使用するときに燃
料ポンプとして図２に例示するような、低比速度の遠心
ポンプ１０を使用している。この図において、１１はイ
ンペラ、１２はシュラウド、１３はケーシング、１４は
軸受、１５はシール（ラビリンスシール）、１６は加圧
前の低圧流体、１７は加圧後の高圧流体である。In the fuel flow rate control device for an aeronautical engine described above, a low specific speed centrifugal pump 10 as shown in FIG. 2 is used as a fuel pump when a large flow rate is used. There is. In this figure, 11 is an impeller, 12 is a shroud, 13 is a casing, 14 is a bearing, 15 is a seal (labyrinth seal), 16 is a low pressure fluid before pressurization, and 17 is a high pressure fluid after pressurization.
【００１０】低比速度の遠心ポンプとは、高回転で大流
量を吐出できるポンプであり、軽量に設計できるため航
空用の場合、その点でメリットが大きい。The low specific speed centrifugal pump is a pump capable of discharging a large flow rate at a high rotation speed and can be designed to be lightweight, so that it has a great advantage in that respect in the case of aviation.
【００１１】しかし、低比速度の遠心ポンプの場合、小
型化のため回転数を高くしているため、円板摩擦が大き
く効率が悪い問題点がある。またそのため、低流量で使
用すると流体の温度が過剰に上昇する問題がある。すな
わち、Ａ．Ｊ．Ｓｔｅｐａｎｏｆｆらの研究によれば、
比速度１００程度の場合、最も大きい損失は円板摩擦で
あり、２０％以上の損失となる。However, in the case of a low specific speed centrifugal pump, since the rotational speed is increased for downsizing, there is a problem that the disk friction is large and the efficiency is low. Therefore, when used at a low flow rate, there is a problem that the temperature of the fluid rises excessively. That is, A. J. According to a study by Stepanoff et al.
When the specific speed is about 100, the largest loss is disc friction, which is 20% or more.
【００１２】本発明はかかる問題点を解決するために創
案されたものである。すなわち、本発明の目的は、円板
摩擦による損失を低減することができ、これにより、低
流量で使用しても流体の温度上昇を抑制することができ
る低損失遠心ポンプを提供することにある。The present invention was created to solve such problems. That is, an object of the present invention is to provide a low-loss centrifugal pump that can reduce the loss due to disc friction and can suppress the temperature rise of the fluid even when used at a low flow rate. .
【００１３】[0013]
【課題を解決するための手段】本発明によれば、液体燃
料を加圧する低比速度の遠心ポンプであって、高速回転
可能なインペラ（１１）のシュラウド（１２）とインペ
ラを囲むケーシング（１３）との間に、インペラと同一
方向に自由回転可能なフローティング部材（２０）を備
える、ことを特徴とする低損失遠心ポンプが提供され
る。According to the present invention, there is provided a low specific speed centrifugal pump for pressurizing liquid fuel, wherein a shroud (12) of an impeller (11) capable of high speed rotation and a casing (13) surrounding the impeller. A low loss centrifugal pump characterized by comprising a floating member (20) freely rotatable in the same direction as the impeller.
【００１４】本発明の好ましい実施形態によれば、前記
フローティング部材（２０）は、シュラウド（１２）と
ケーシング（１３）との間で非接触に回転可能なフロー
ティングディスク（２１、２２）と、該フローティング
ディスクとケーシング（１３）との隙間を液密にシール
するシール部材（２１ａ，２１ｂ，２２ａ，２２ｂ）と
からなる。According to a preferred embodiment of the present invention, the floating member (20) includes a floating disk (21, 22) rotatable between the shroud (12) and the casing (13) in a non-contact manner. It comprises a seal member (21a, 21b, 22a, 22b) for sealing the gap between the floating disk and the casing (13) in a liquid-tight manner.
【００１５】円板摩擦は、ケーシングとシュラウドの相
対速度の二乗に比例するため、相対速度を半分にするデ
ィスクをケーシングとシュラウドの間に入れれば、円板
摩擦の生じる面積は２倍になるが、円板摩擦が１／４に
なるため、全体で損失が１／２になる。Since the disc friction is proportional to the square of the relative velocity between the casing and the shroud, if a disc that halves the relative velocity is inserted between the casing and the shroud, the area where the disc friction occurs is doubled. Since the disc friction becomes 1/4, the loss becomes 1/2 as a whole.
【００１６】[0016]
【発明の実施の形態】以下、本発明の好ましい実施形態
を図面を参照して説明する。なお、各図において、共通
する部分には同一の符号を付し、重複した説明を省略す
る。BEST MODE FOR CARRYING OUT THE INVENTION Preferred embodiments of the present invention will be described below with reference to the drawings. In each drawing, common portions are denoted by the same reference numerals, and redundant description will be omitted.
【００１７】図１は、本発明による低損失遠心ポンプの
構成図である。この図において、本発明の低損失遠心ポ
ンプは、液体燃料を加圧する低比速度の遠心ポンプであ
る。また、本発明の低損失遠心ポンプは、高速回転可能
なインペラ１１のシュラウド１２とインペラを囲むケー
シング１３との間に、インペラ１１と同一方向に自由回
転可能なフローティング部材２０を備える。FIG. 1 is a block diagram of a low loss centrifugal pump according to the present invention. In this figure, the low loss centrifugal pump of the present invention is a low specific speed centrifugal pump that pressurizes liquid fuel. Further, the low-loss centrifugal pump of the present invention includes a floating member 20 freely rotatable in the same direction as the impeller 11 between the shroud 12 of the impeller 11 that can rotate at high speed and the casing 13 that surrounds the impeller.
【００１８】フローティング部材２０は、この例では、
シュラウド１２とケーシング１３との間で非接触に回転
可能なフローティングディスク２１、２２と、これらの
フローティングディスク２１、２２とケーシング１３と
の隙間を液密にシールするシール部材２１ａ，２１ｂ，
２２ａ，２２ｂとからなる。シール部材２１ａ，２１
ｂ，２２ａ，２２ｂはこの例ではラビリンスシールであ
る。The floating member 20 is, in this example,
Floating disks 21 and 22 that can rotate in a non-contact manner between the shroud 12 and the casing 13, and sealing members 21a and 21b that seal the gaps between the floating disks 21 and 22 and the casing 13 in a liquid-tight manner.
22a and 22b. Seal members 21a, 21
b, 22a and 22b are labyrinth seals in this example.
【００１９】図２に示した従来の低比速度の遠心ポンプ
の場合、Ａ．Ｊ．Ｓｔｅｐａｎｏｆｆらの研究によれ
ば、比速度１００程度の場合、最も大きい損失は円板摩
擦であり、２０％以上の損失となる。また、これはイン
ペラ１１のシュラウド１２（円盤状の羽根を覆う板）と
流体の摩擦によるものであり回転速度の２乗に比例す
る。またこの円板摩擦は図２に太い破線１８で示す４ケ
所部分で発生する。この円板摩擦部分１８は、この例で
はすべて高圧流体内であり円板摩擦も大きくなってい
る。In the case of the conventional low specific speed centrifugal pump shown in FIG. J. According to the study by Stepanoff et al., When the specific speed is about 100, the largest loss is disk friction, which is 20% or more. Further, this is due to the friction between the shroud 12 (the plate covering the disk-shaped blades) of the impeller 11 and the fluid, and is proportional to the square of the rotation speed. Further, this disc friction occurs at the four places indicated by the thick broken line 18 in FIG. In this example, the disc friction portion 18 is entirely in the high pressure fluid, and the disc friction is large.
【００２０】シュラウド１２と流体の相対速度を１／２
にできれば、円盤摩擦はその二乗の１／４に減少する。
この効果を得るために、図１に示した装置では、シュラ
ウド１２（インペラ回転数）とケーシング１３（回転
数：０）との間にフリーに回転する円盤（フローティン
グディスク）を挿入している。Halve the relative velocity of the shroud 12 and the fluid
If possible, the disk friction will be reduced to 1/4 of its square.
In order to obtain this effect, in the apparatus shown in FIG. 1, a freely rotating disk (floating disk) is inserted between the shroud 12 (impeller rotation speed) and the casing 13 (rotation speed: 0).
【００２１】この構成により、シュラウド１２とフリー
円盤（フローティングディスク）の相対速度が約１／２
となり、ケーシング１３とフローティングディスクとの
相対速度も約１／２となる。すなわちフローティングデ
ィスク２１、２２は、その両面に作用する摩擦抵抗が一
致する速度、言い換えれば損失エネルギーが最小となる
速度で回転し、両面の面積が同一の場合、その速度はイ
ンペラ回転数の約１／２となる。With this configuration, the relative speed between the shroud 12 and the free disk (floating disk) is about 1/2.
Therefore, the relative speed between the casing 13 and the floating disk is also about 1/2. That is, the floating disks 21 and 22 rotate at a speed at which the frictional resistances acting on both surfaces match, in other words, at a speed at which the energy loss is minimized, and when the areas on both surfaces are the same, the speed is about 1 of the impeller rotation speed. / 2.
【００２２】図１において、フローティングディスク２
１、２２は受圧面（４ケ所の円板摩擦部分１８）の釣り
合いにより、どの部材とも接触しておらず、流体の摩擦
だけにより駆動される。In FIG. 1, the floating disk 2
1 and 22 are not in contact with any member due to the balance of the pressure receiving surfaces (the disc friction portions 18 at the four places), and are driven only by the friction of the fluid.
【００２３】シール部材（ラビリンスシール）２１ａ，
２１ｂ，２２ａ，２２ｂにより、フローティングディス
ク２１、２２の外面は、高圧流体１７と低圧流体１６の
中間圧力、すなわち外側シール部材２１ａ，２２ａと内
側シール部材２１ｂ，２２ｂを通して高圧から低圧まで
に抜ける中間圧力を受ける。従ってこの中間圧力によ
り、フローティングディスク２１、２２は、インペラ１
１のシュラウド１２に向けて押し付けられる。A seal member (labyrinth seal) 21a,
21b, 22a, 22b cause the outer surfaces of the floating disks 21, 22 to have an intermediate pressure between the high-pressure fluid 17 and the low-pressure fluid 16, that is, an intermediate pressure at which high pressure to low pressure is released through the outer seal members 21a, 22a and inner seal members 21b, 22b. Receive. Therefore, this intermediate pressure causes the floating disks 21 and 22 to move to the impeller 1
It is pressed toward the shroud 12 of 1.
【００２４】一方、フローティングディスク２１、２２
の内面は、この例では高圧流体１７の圧力を受け、イン
ペラ１１のシュラウド１２から遠ざかる方向に力を受け
る。On the other hand, the floating disks 21, 22
The inner surface of is subjected to the pressure of the high-pressure fluid 17 in this example, and is subjected to a force in a direction away from the shroud 12 of the impeller 11.
【００２５】フローティングディスク２１、２２の外面
圧力は、シュラウド１２に近づいたとき内側シール部材
２１ｂ，２２ｂが開き外側シール部材２１ａ，２２ａを
流れる流量も増えて中間圧力が下がる。またシュラウド
１２から遠ざかったときに、内側シール部材２１ｂ，２
２ｂが閉まり、リークが減り圧力が上がる。また、内側
シール部材２１ｂ，２２ｂのリークが０となったときフ
ローティングディスク２１、２２の外面圧力は中間圧力
と同圧になる。The outer surface pressure of the floating disks 21, 22 is such that when the shroud 12 is approached, the inner seal members 21b, 22b are opened and the flow rate of the outer seal members 21a, 22a is increased to lower the intermediate pressure. Also, when the shroud 12 is moved away from the inner seal members 21b, 2
2b closes, leaks decrease and pressure rises. Further, when the leakage of the inner seal members 21b and 22b becomes 0, the outer surface pressure of the floating disks 21 and 22 becomes the same as the intermediate pressure.
【００２６】このような関係によりリークが０でないど
こかのリーク量で、部材は完全にどこにも接していない
状態で圧力がバランスする点で静止する。なお、径方向
にも圧力バランス溝等を設けることによって、径方向も
どこにも接していない状態にすることが可能である。こ
の構成により、フローティングディスク２１、２２は、
ポンプによって生じる流体の回転の摩擦のトルクにより
自転する。Due to such a relationship, when the leak amount is somewhere other than zero, the member is stationary at a point where the pressure is balanced without being completely in contact with anything. By providing a pressure balance groove or the like in the radial direction as well, it is possible to make a state in which no pressure contact groove is in contact with the radial direction either. With this configuration, the floating disks 21 and 22 are
The rotation of the fluid caused by the pump causes the friction torque to rotate on its axis.
【００２７】円板摩擦は、ケーシングとシュラウドの相
対速度の二乗に比例するため、上述したフローティング
ディスク２１、２２をケーシング１３とシュラウド１２
の間に入れることにより、円板摩擦の生じる面積は２倍
になるが、円板摩擦が１／２の二乗の１／４になるた
め、全体で損失が１／２になる。従って、低比速度の遠
心ポンプの効率が向上し、低流量域まで使用できるよう
になる。Since the disc friction is proportional to the square of the relative velocity of the casing and the shroud, the above-mentioned floating disks 21 and 22 are attached to the casing 13 and the shroud 12.
By inserting it in between, the area where the disc friction occurs is doubled, but since the disc friction becomes 1/4 of the square of 1/2, the loss becomes 1/2 as a whole. Therefore, the efficiency of the low specific speed centrifugal pump is improved and the low flow rate region can be used.
【００２８】なお本発明は以上に述べた実施形態に限ら
れるものではなく、発明の要旨を逸脱しない範囲で各種
の変更が可能である。The present invention is not limited to the embodiments described above, and various modifications can be made without departing from the gist of the invention.
【００２９】[0029]
【発明の効果】上述したように、本発明の低損失遠心ポ
ンプは、円板摩擦による損失を低減することができ、こ
れにより、低流量で使用しても流体の温度上昇を抑制す
ることができる等の優れた効果を有する。As described above, the low-loss centrifugal pump of the present invention can reduce the loss due to the disc friction, and thus suppress the temperature rise of the fluid even when used at a low flow rate. It has an excellent effect such as being able to.
【図１】本発明による低損失遠心ポンプの構成図であ
る。FIG. 1 is a configuration diagram of a low loss centrifugal pump according to the present invention.
【図２】従来の低損失遠心ポンプの構成図である。FIG. 2 is a configuration diagram of a conventional low-loss centrifugal pump.
【図３】従来の燃料流量制御装置の構成図である。FIG. 3 is a configuration diagram of a conventional fuel flow rate control device.
【符号の説明】
１ 燃料ポンプ、２ 計量バルブ、３ ドレインバル
ブ、４ ノズル、５ バイパスバルブ、６ 差圧センサ
ーバルブ、７ａ，７ｂ パイロットライン、８ａ，８
ｂ，８ｃ パイロットライン、９ａ，９ｂ バイパスラ
イン、１０ 遠心ポンプ、１１ インペラ、１２ シュ
ラウド、１３ ケーシング、１４ 軸受、１５ シール
（ラビリンスシール）、１６ 低圧流体、１７ 高圧流
体、２０ フローティング部材、２１、２２ フローテ
ィングディスク、２１ａ，２１ｂ，２２ａ，２２ｂ シ
ール部材（ラビリンスシール）[Explanation of reference numerals] 1 fuel pump, 2 metering valve, 3 drain valve, 4 nozzle, 5 bypass valve, 6 differential pressure sensor valve, 7a, 7b pilot line, 8a, 8
b, 8c Pilot line, 9a, 9b Bypass line, 10 Centrifugal pump, 11 Impeller, 12 Shroud, 13 Casing, 14 Bearing, 15 Seal (labyrinth seal), 16 Low pressure fluid, 17 High pressure fluid, 20 Floating member, 21, 22 Floating disk, 21a, 21b, 22a, 22b Seal member (labyrinth seal)
───────────────────────────────────────────────────── フロントページの続き Ｆターム(参考） 3H022 AA01 BA02 BA07 CA21 CA22 CA32 CA56 DA08 3H033 AA01 AA15 AA16 BB01 BB06 BB11 CC04 CC07 DD01 DD29 DD30 EE09 EE13 3H034 AA01 AA15 AA16 BB01 BB06 BB11 CC04 CC07 DD01 DD28 DD30 EE09 EE13 ─────────────────────────────────────────────────── ─── Continued front page F term (reference) 3H022 AA01 BA02 BA07 CA21 CA22 CA32 CA56 DA08 3H033 AA01 AA15 AA16 BB01 BB06 BB11 CC04 CC07 DD01 DD29 DD30 EE09 EE13 3H034 AA01 AA15 AA16 BB01 BB06 BB11 CC04 CC07 DD01 DD28 DD30 EE09 EE13
Claims (2)
プであって、高速回転可能なインペラ（１１）のシュラ
ウド（１２）とインペラを囲むケーシング（１３）との
間に、インペラと同一方向に自由回転可能なフローティ
ング部材（２０）を備える、ことを特徴とする低損失遠
心ポンプ。1. A low specific speed centrifugal pump for pressurizing liquid fuel, which is provided between a shroud (12) of an impeller (11) capable of high speed rotation and a casing (13) surrounding the impeller in the same direction as the impeller. A low-loss centrifugal pump, comprising a freely rotatable floating member (20).
ュラウド（１２）とケーシング（１３）との間で非接触
に回転可能なフローティングディスク（２１、２２）
と、該フローティングディスクとケーシング（１３）と
の隙間を液密にシールするシール部材（２１ａ，２１
ｂ，２２ａ，２２ｂ）とからなる、ことを特徴とする請
求項１に記載の低損失遠心ポンプ。2. The floating member (20) is a floating disk (21, 22) rotatable in a non-contact manner between the shroud (12) and the casing (13).
And sealing members (21a, 21a) for sealing the gap between the floating disk and the casing (13) in a liquid-tight manner.
b, 22a, 22b), The low-loss centrifugal pump according to claim 1, characterized in that
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001207312A JP4807542B2 (en) | 2001-07-09 | 2001-07-09 | Low loss centrifugal pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001207312A JP4807542B2 (en) | 2001-07-09 | 2001-07-09 | Low loss centrifugal pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2003021096A true JP2003021096A (en) | 2003-01-24 |
| JP4807542B2 JP4807542B2 (en) | 2011-11-02 |
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ID=19043318
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001207312A Expired - Lifetime JP4807542B2 (en) | 2001-07-09 | 2001-07-09 | Low loss centrifugal pump |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP4807542B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007273009A (en) * | 2006-03-31 | 2007-10-18 | Saxa Inc | Disk device |
| JP2010216374A (en) * | 2009-03-17 | 2010-09-30 | Kawasaki Heavy Ind Ltd | Hydraulic power generating device |
| ITFI20120210A1 (en) * | 2012-10-15 | 2014-04-16 | Nuovo Pignone Srl | "HIGH EFFICIENCY LOW SPECIFIC SPEED CENTRIFUGAL PUMP" |
| KR20140070251A (en) * | 2012-11-30 | 2014-06-10 | 삼성테크윈 주식회사 | Impeller |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57126593U (en) * | 1981-01-31 | 1982-08-06 |
-
2001
- 2001-07-09 JP JP2001207312A patent/JP4807542B2/en not_active Expired - Lifetime
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS57126593U (en) * | 1981-01-31 | 1982-08-06 |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007273009A (en) * | 2006-03-31 | 2007-10-18 | Saxa Inc | Disk device |
| JP2010216374A (en) * | 2009-03-17 | 2010-09-30 | Kawasaki Heavy Ind Ltd | Hydraulic power generating device |
| ITFI20120210A1 (en) * | 2012-10-15 | 2014-04-16 | Nuovo Pignone Srl | "HIGH EFFICIENCY LOW SPECIFIC SPEED CENTRIFUGAL PUMP" |
| WO2014060343A1 (en) * | 2012-10-15 | 2014-04-24 | Nuovo Pignone Srl | High efficiency low specific speed centrifugal pump |
| KR20150070294A (en) * | 2012-10-15 | 2015-06-24 | 누보 피그노네 에스알엘 | High efficiency low specific speed centrifugal pump |
| CN104813033A (en) * | 2012-10-15 | 2015-07-29 | 诺沃皮尼奥内股份有限公司 | High efficiency low specific speed centrifugal pump |
| US20150260190A1 (en) * | 2012-10-15 | 2015-09-17 | Nuovo Pignone Srl | High efficiency low specific speed centrifugal pump |
| JP2015532389A (en) * | 2012-10-15 | 2015-11-09 | ヌオーヴォ ピニォーネ ソチエタ レスポンサビリタ リミタータＮｕｏｖｏ Ｐｉｇｎｏｎｅ Ｓ．Ｒ．Ｌ． | High efficiency low specific speed centrifugal pump |
| AU2013331741B2 (en) * | 2012-10-15 | 2017-06-08 | Nuovo Pignone Tecnologie - S.R.L. | High efficiency low specific speed centrifugal pump |
| KR102200789B1 (en) * | 2012-10-15 | 2021-01-13 | 누보 피그노네 에스알엘 | High efficiency low specific speed centrifugal pump |
| KR20140070251A (en) * | 2012-11-30 | 2014-06-10 | 삼성테크윈 주식회사 | Impeller |
| KR101960714B1 (en) * | 2012-11-30 | 2019-03-22 | 한화파워시스템 주식회사 | Impeller |
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| Publication number | Publication date |
|---|---|
| JP4807542B2 (en) | 2011-11-02 |
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