JP5839803B2 - Bypass energy recovery device for fluid machinery - Google Patents

Bypass energy recovery device for fluid machinery Download PDF

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JP5839803B2
JP5839803B2 JP2011011525A JP2011011525A JP5839803B2 JP 5839803 B2 JP5839803 B2 JP 5839803B2 JP 2011011525 A JP2011011525 A JP 2011011525A JP 2011011525 A JP2011011525 A JP 2011011525A JP 5839803 B2 JP5839803 B2 JP 5839803B2
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pressure loss
energy recovery
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pressure
flow path
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JP2012154186A (en
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真成 飯野
真成 飯野
佐野　岳志
岳志 佐野
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Mitsubishi Heavy Industries Ltd
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    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
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Description

本発明は、例えばポンプ・水車等流体機械のバイパスエネルギ回収装置に関する。   The present invention relates to a bypass energy recovery device for a fluid machine such as a pump or a water turbine.

一般に、ポンプ・水車等流体（液体）機械では、単段・多段を問わず、スラスト力バランスやミニフロー（低流量域）でのポンプ特性（不安定性や振動）をコントロールするため、主流路の高圧側から分岐して低圧側に通じるバイパス流路を設けているが、このバイパス流量をコントロールするのに、オリフィスや狭路により圧力損失（以下、圧損という）を与える方式を採用している。   Generally, in fluid (liquid) machines such as pumps and water turbines, regardless of whether they are single-stage or multi-stage, in order to control the thrust force balance and pump characteristics (instability and vibration) in the mini-flow (low flow area), A bypass flow path that branches from the high-pressure side and leads to the low-pressure side is provided. In order to control this bypass flow rate, a system that applies pressure loss (hereinafter referred to as pressure loss) by an orifice or narrow path is adopted.

例えば、特許文献１で開示された多段遠心ポンプにおいては、吐出側から吸込側へ向けたポンプ内部バイパス用穴を設けて、ポンプ流量を増加させることなくポンプ内部でのバイパス流量を増加させることで低流量域運転時の異常圧力脈動を低減するようにしている。即ち、ポンプ最少流量を増加させることによるプラントシステム側への悪影響をなくしているのである。   For example, in the multistage centrifugal pump disclosed in Patent Document 1, by providing a pump internal bypass hole from the discharge side to the suction side, the bypass flow rate inside the pump is increased without increasing the pump flow rate. Abnormal pressure pulsation during low flow rate operation is reduced. That is, the adverse effect on the plant system side by increasing the pump minimum flow rate is eliminated.

また、特許文献２で開示された多段遠心ポンプにおいては、インペラに作用する軸方向スラストをバランスさせるため、最終段のインペラの背側の高圧の液体をシール部で絞ることにより減圧してバランスディスクの高圧側室に導入し、この高圧側室の圧力を軸方向隙間により圧損を調節することで制御している。さらに、本特許文献２では、バランスディスクの高圧側に高圧側室内の液体を付勢してその圧力を上昇させる複数の羽根を設けている。   In the multistage centrifugal pump disclosed in Patent Document 2, in order to balance the axial thrust acting on the impeller, the balance disk is depressurized by squeezing the high-pressure liquid on the back side of the impeller at the final stage at the seal portion. The pressure in the high pressure side chamber is controlled by adjusting the pressure loss by the axial clearance. Furthermore, in this patent document 2, the several blade | wing which energizes the liquid in a high pressure side chamber and raises the pressure is provided in the high pressure side of the balance disk.

実開昭６３−６７６９３号公報Japanese Utility Model Publication No. 63-67693 特開平１１−８２３６４号公報Japanese Patent Laid-Open No. 11-82364

このように、特許文献１及び２においては、主流路の高圧側から分岐して低圧側に通じるバイパス流路を流れるバイパス流量をコントロールする方法としてオリフィスや狭路により圧損を与える方式を採用しているが、減圧（圧損）分の流体エネルギは、従来、回収することなく無駄に失っていた。特に、特許文献２では、バランスディスクの高圧側に複数の羽根を設けて加圧するというエネルギ「供給」方式については開示されているが、そもそも捨てているエネルギを有効活用するという技術思想は一切開示されていない。   As described above, in Patent Documents 1 and 2, a method of applying pressure loss by an orifice or a narrow path is adopted as a method of controlling the bypass flow rate that flows through the bypass flow path branched from the high pressure side of the main flow path to the low pressure side. However, conventionally, the fluid energy corresponding to the reduced pressure (pressure loss) has been lost without being recovered. In particular, Patent Document 2 discloses an energy “supply” method in which a plurality of blades are provided on the high-pressure side of a balance disk to pressurize, but the technical idea of effectively utilizing the energy that has been discarded is not disclosed at all. It has not been.

そこで、本発明は、圧損機構における減圧（圧損）分の流体エネルギを有効活用して機器のトータル効率を向上させることができる流体機械のバイパスエネルギ回収装置を提供することを目的とする。   Therefore, an object of the present invention is to provide a bypass energy recovery device for a fluid machine that can effectively use the fluid energy corresponding to the pressure reduction (pressure loss) in the pressure loss mechanism to improve the total efficiency of the device.

斯かる目的を達成するための本発明に係る流体機械のバイパスエネルギ回収装置は、
主流路の高圧側から分岐して低圧側に通じるバイパス流路に圧損機構を備えた流体機械において、
前記バイパス流路に、前記圧損機構における圧損エネルギを回収するための圧損エネルギ回収手段を設け、
前記流体機械と前記圧損エネルギ回収手段が別軸であり、
前記圧損エネルギ回収手段は、遠心ポンプにおけるバランスディスクの圧力調整部水路に設置したハイドロタービンである
ことを特徴とする。 In order to achieve such an object, a bypass energy recovery device for a fluid machine according to the present invention comprises:
In a fluid machine having a pressure loss mechanism in a bypass channel that branches from the high pressure side of the main channel and leads to the low pressure side,
A pressure loss energy recovery means for recovering pressure loss energy in the pressure loss mechanism is provided in the bypass flow path,
The fluid machine and the pressure loss energy recovery means Ri another axial der,
The pressure loss energy recovery means is a hydro turbine installed in a water pressure channel of a balance disk of a balance disk in a centrifugal pump .

本発明に係るバイパスエネルギ回収装置によれば、圧損機構における圧損エネルギを圧損エネルギ回収手段により回収するようにしたので、圧損機構における圧損分の流体エネルギを有効活用して機器のトータル効率を向上させることができる。   According to the bypass energy recovery device of the present invention, since the pressure loss energy in the pressure loss mechanism is recovered by the pressure loss energy recovery means, the fluid energy corresponding to the pressure loss in the pressure loss mechanism is effectively used to improve the total efficiency of the device. be able to.

本発明の実施例１を示すバイパスエネルギ回収装置を備えた多段遠心ポンプの流体流れ説明図である。It is fluid flow explanatory drawing of the multistage centrifugal pump provided with the bypass energy recovery apparatus which shows Example 1 of this invention. パワージェネレータの異なった具体例を示す各々の概略構成図である。It is each schematic block diagram which shows the specific example from which a power generator differs. 本発明の実施例２を示すバイパスエネルギ回収装置を備えた多段遠心ポンプの流体流れ説明図である。It is fluid flow explanatory drawing of the multistage centrifugal pump provided with the bypass energy recovery apparatus which shows Example 2 of this invention. 本発明の実施例３を示すバイパスエネルギ回収装置を備えた多段遠心ポンプの流体流れ説明図である。It is fluid flow explanatory drawing of the multistage centrifugal pump provided with the bypass energy recovery apparatus which shows Example 3 of this invention. 本発明の実施例４を示すバイパスエネルギ回収装置を備えた多段遠心ポンプの要部断面図である。It is principal part sectional drawing of the multistage centrifugal pump provided with the bypass energy recovery apparatus which shows Example 4 of this invention.

以下、本発明に係る流体機械のバイパスエネルギ回収装置を実施例により図面を用いて詳細に説明する。   DESCRIPTION OF EMBODIMENTS Hereinafter, a bypass energy recovery device for a fluid machine according to the present invention will be described in detail with reference to the drawings by way of examples.

図１は本発明の実施例１を示すバイパスエネルギ回収装置を備えた多段遠心ポンプの流体流れ説明図、図２はパワージェネレータの異なった具体例を示す各々の概略構成図である。   FIG. 1 is an explanatory diagram of a fluid flow of a multistage centrifugal pump including a bypass energy recovery device according to a first embodiment of the present invention, and FIG. 2 is a schematic configuration diagram showing different specific examples of a power generator.

図１に示すように、多段遠心ポンプの主軸１０上には、中間（センター）ブシュ１１を境に吸込口１２側に１段から５段のインペラが固設されると共に吐出口１３側に、１段から５段のインペラにおける内部流体の流れ方向とは反対の流れ方向となるように、６段から１０段のインペラが固設される。   As shown in FIG. 1, on the main shaft 10 of the multi-stage centrifugal pump, 1 to 5 stage impellers are fixed on the suction port 12 side with an intermediate (center) bush 11 as a boundary, and on the discharge port 13 side, The 6th to 10th stage impellers are fixed so that the flow direction is opposite to the flow direction of the internal fluid in the 1st to 5th stage impellers.

そして、吸込口１２から１段→１０段のインペラを経て吐出口１３に至る流体の主流路１４（これは、１段から５段のインペラ間の第１流路１４ａと６段から１０段のインペラ間の第２流路１４ｂとからなる）の他に、１０段のインペラから５段のインペラへと内部流体を戻す戻り流路１５が中間ブシュ１１に形成されると共に、６段のインペラ手前からつり合いブシュ１６に形成された戻り流路１７を経て１段のインペラへ内部流体を戻すつり合い管（バイパス流路）１８が設けられる。更に、前記主流路１４における１０段のインペラ下流側と１段のインペラ上流側とを結ぶ内部バイパス用配管（バイパス流路）１９が設けられる。 The main flow path 14 of fluid from the suction port 12 to the discharge port 13 through the first stage → 10th stage impeller (this is the first flow path 14a between the first stage to the fifth stage impeller and the sixth stage to the 10th stage In addition to the second flow path 14b between the impellers, a return flow path 15 for returning the internal fluid from the 10-stage impeller to the 5-stage impeller is formed in the intermediate bush 11, and the 6-stage impeller A counterbalance pipe (bypass channel) 18 for returning the internal fluid to the first stage impeller through a return channel 17 formed in the counterbalance bush 16 from the front is provided. Furthermore, an internal bypass pipe (bypass flow path) 19 that connects the 10th stage impeller downstream side and the 1st stage impeller upstream side in the main flow path 14 is provided.

前記内部バイパス用配管１９に、圧損機構兼圧損エネルギ回収手段としてのパワージェネレータ２０が介装される。このパワージェネレータ２０としては、図２に示すように、フランシス型のランナー２１ａを備えた水車２２ａで発電機２３ａを駆動するもの（図２の(ａ)）、プロペラ型のランナー２１ｂを備えた水車２２ｂで発電機２３ｂを駆動するもの（図２の(ｂ)）やフランシス型のランナー２１ａ（プロペラ型のランナー２１ｂでも良い）を備えた二つの水車２２ａをタンデム等に繋いで発電機２３ａを駆動するもの（図２の(ａ)）等を用いると好適である。   A power generator 20 as a pressure loss mechanism / pressure loss energy recovery means is interposed in the internal bypass pipe 19. As this power generator 20, as shown in FIG. 2, a generator 22a is driven by a turbine 22a provided with a Francis-type runner 21a (FIG. 2A), and a turbine provided with a propeller-type runner 21b. The generator 23a is driven by connecting two turbines 22a, which are equipped with a 22b to drive the generator 23b ((b) of FIG. 2) or a Francis-type runner 21a (or a propeller-type runner 21b) to a tandem or the like. It is preferable to use what to do ((a) in FIG. 2).

このように構成されるため、多段遠心ポンプの低流量域運転時には、先ず、プラントシステム側からポンプ流量Ｑが主流路１４に対し給排される。そして、１段から５段のインペラ間の主流路１４（第１流路１４ａ）には、前記ポンプ流量Ｑに加えて戻り流路１７及びつり合い管１８からのバイパス流量ｑ1と内部バイパス用配管１９からのバイパス流量ｑ3とが増加されて流れる。一方、６段から１０段のインペラ間の主流路１４（第２流路１４ｂ）には、前記ポンプ流量Ｑに加えて戻り流路１５からのバイパス流量ｑ2と内部バイパス用配管１９からのバイパス流量ｑ3とが増加されて流れる。   Since it is configured in this way, when the multistage centrifugal pump is operated in a low flow rate region, first, the pump flow rate Q is supplied to and discharged from the main flow path 14 from the plant system side. In addition to the pump flow rate Q, the bypass flow rate q1 from the return flow channel 17 and the balance pipe 18 and the internal bypass pipe 19 are provided in the main flow path 14 (first flow path 14a) between the first to fifth impellers. And the bypass flow rate q3 from is increased. On the other hand, in the main flow path 14 (second flow path 14b) between the 6th to 10th impellers, in addition to the pump flow Q, the bypass flow q2 from the return flow path 15 and the bypass flow from the internal bypass pipe 19 are used. q3 is increased and flows.

これにより、ポンプ流量Ｑを増加させることなくポンプ内部でのバイパス流量ｑ1，ｑ2，ｑ3を増加させることで、１段から１０段のインペラにおける実質的な流量増加が図られ、低流量域運転時の異常圧力脈動を効果的に低減させられる。即ち、ポンプ実質流量を増加させることによりプラントシステム側への悪影響をなくすことができるのである。また、戻り流路１７及びつり合い管１８からのバイパス流量ｑ1により、１段から１０段のインペラに作用する軸方向スラストをバランスさせられる。   As a result, by increasing the bypass flow rates q1, q2, and q3 inside the pump without increasing the pump flow rate Q, a substantial increase in the flow rate in the 1st to 10th stage impellers can be achieved. The abnormal pressure pulsation can be effectively reduced. That is, the adverse effect on the plant system side can be eliminated by increasing the pump actual flow rate. Further, the axial thrust acting on the first to tenth impellers can be balanced by the bypass flow rate q1 from the return flow path 17 and the balance pipe 18.

そして、本実施例では、内部バイパス用配管１９に圧損機構兼圧損エネルギ回収手段としてのパワージェネレータ２０を介装したので、圧損機構における圧損エネルギをパワージェネレータ２０により回収することができ、圧損機構における圧損分の流体エネルギを有効活用して多段遠心ポンプのトータル効率を向上させることができる。   In this embodiment, since the power generator 20 as the pressure loss mechanism / pressure loss energy recovery means is interposed in the internal bypass pipe 19, the pressure loss energy in the pressure loss mechanism can be recovered by the power generator 20, and in the pressure loss mechanism The total efficiency of the multistage centrifugal pump can be improved by effectively utilizing the fluid energy corresponding to the pressure loss.

図３Ａは本発明の実施例２を示すバイパスエネルギ回収装置を備えた多段遠心ポンプの流体流れ説明図である。   FIG. 3A is an explanatory diagram of fluid flow of a multistage centrifugal pump including a bypass energy recovery device according to Embodiment 2 of the present invention.

これは、実施例１における内部バイパス用配管１９に、フランシス型のランナー２５ａ（プロペラ型のランナーでも良い）を備えたハイドロタービン（圧損機構兼圧損エネルギ回収手段）２５を、主軸１０に直接連携させて配置した例であり、その他の構成は図１と同様なので図１と同一部材には同一符号を付して重複する説明は省略する。   This is because a hydro turbine (pressure loss mechanism / pressure loss energy recovery means) 25 provided with a Francis type runner 25a (propeller type runner) may be directly linked to the main shaft 10 in the internal bypass pipe 19 in the first embodiment. The other components are the same as those shown in FIG. 1, and the same members as those shown in FIG.

これによれば、圧損機構における圧損エネルギをハイドロタービン２５により軸動力として回収することができ、実施例１と同様の作用効果が得られる。   According to this, the pressure loss energy in the pressure loss mechanism can be recovered as shaft power by the hydro turbine 25, and the same effect as the first embodiment can be obtained.

図３Ｂは本発明の実施例３を示すバイパスエネルギ回収装置を備えた多段遠心ポンプの流体流れ説明図である。   FIG. 3B is a fluid flow explanatory diagram of a multistage centrifugal pump including a bypass energy recovery device according to a third embodiment of the present invention.

これは、実施例１における内部バイパス用配管１９に、フランシス型のランナー２５ａ（プロペラ型のランナーでも良い）を備えた例えば二つの（一つ以上であれば良い）ハイドロタービン（圧損機構兼圧損エネルギ回収手段）２５を回転軸２５ｂ上にタンデムに繋いで配置し、この回転軸２５ｂをギアボックス（変速機）２６を介して主軸１０に間接的に連携させた例であり、その他の構成は図１と同様なので図１と同一部材には同一符号を付して重複する説明は省略する。   This is because, for example, two (or more) hydroturbines (pressure loss mechanism and pressure loss energy) provided with the Francis type runner 25a (may be a propeller type runner) in the internal bypass pipe 19 in the first embodiment. (Collecting means) 25 is arranged in tandem on the rotary shaft 25b, and this rotary shaft 25b is indirectly linked to the main shaft 10 via a gear box (transmission) 26. 1, the same members as those in FIG.

これによれば、圧損機構における圧損エネルギを例えば二つの（一つ以上であれば良い）ハイドロタービン（圧損機構兼圧損エネルギ回収手段）２５により軸動力として回収することができ、実施例１と同様の作用効果が得られる。   According to this, the pressure loss energy in the pressure loss mechanism can be recovered as shaft power by, for example, two (one or more) hydro turbines (pressure loss mechanism / pressure loss energy recovery means) 25, as in the first embodiment. The following effects can be obtained.

図４は本発明の実施例４を示すバイパスエネルギ回収装置を備えた多段遠心ポンプの要部断面図である。   FIG. 4 is a cross-sectional view of a main part of a multistage centrifugal pump equipped with a bypass energy recovery device showing Embodiment 4 of the present invention.

これは、中間ケーシング３９と吐出ケーシング４０内に横架された主軸３０上に複数のインペラ３１とこれらインペラ３１に作用する軸方向スラストをバランスするためのバランスディスク３２を固定してなる多段遠心ポンプにおいて、バランスディスク３２のディスク隙間（圧力調整部水路：バイパス流路）３５に圧損エネルギ回収手段としてのハイドロタービン（羽根車）３８を設置した例である。   This is a multistage centrifugal pump in which a plurality of impellers 31 and a balance disk 32 for balancing axial thrust acting on the impellers 31 are fixed on a main shaft 30 that is horizontally mounted in an intermediate casing 39 and a discharge casing 40. In this example, a hydro turbine (impeller) 38 as pressure loss energy recovery means is installed in a disk gap (pressure adjusting unit water channel: bypass channel) 35 of the balance disk 32.

具体的には、多段遠心ポンプの運転時、ディスク隙間３５手前の高圧側室３４には最終段のインペラ３１の背側からインペラ３１によって圧力Ｐ1から圧力Ｐ2へ昇圧された液体がシール部３３で圧力Ｐ3に減圧されて供給される。図示例では、バランスディスク３２の高圧側に高圧側室３４内の液体を付勢してその圧力Ｐ3を上昇させる複数の羽根３７を設けているがこれは特に設けなくても良い。そして、この圧力Ｐ3の液体の一部はディスク隙間３５を通りバランスディスク３２の外周面のシール部３６を流過することにより圧力Ｐ0に減圧されて低圧側室４２内に入り、バランス管４１を経て流出する。 Specifically, when the multistage centrifugal pump is in operation, the high pressure side chamber 34 in front of the disk gap 35 is filled with the liquid pressurized from the pressure P 1 to the pressure P 2 by the impeller 31 from the back side of the final stage impeller 31. in supplied pressure is reduced to a pressure P 3. In the illustrated example, a plurality of blades 37 are provided on the high pressure side of the balance disk 32 to urge the liquid in the high pressure side chamber 34 to increase its pressure P 3 , but this need not be provided. A part of the liquid having the pressure P 3 passes through the disk gap 35 and flows through the seal portion 36 on the outer peripheral surface of the balance disk 32 to be reduced to the pressure P 0 and enter the low pressure side chamber 42. It flows out through.

これによって、インペラ３１の背側の圧力Ｐ2によりインペラ３１に作用する吸込側へのスラスト力が高圧側室３４内の圧力Ｐ3によりバランスディスク３２に作用する低圧側室４２へのスラスト力とバランスさせられる。 Thereby, the thrust force to the suction side acting on the impeller 31 by the pressure P 2 on the back side of the impeller 31 is balanced with the thrust force to the low pressure side chamber 42 acting on the balance disk 32 by the pressure P 3 in the high pressure side chamber 34. It is done.

そして、本実施例では、圧損機構を構成するディスク隙間３５に圧損エネルギ回収手段としてのハイドロタービン３８を設置したので、圧損機構における圧損エネルギをハイドロタービン３８により軸動力として回収することができ、圧損機構における圧損分の流体エネルギを有効活用して多段遠心ポンプのトータル効率を向上させることができる。   In this embodiment, since the hydro turbine 38 as pressure loss energy recovery means is installed in the disk gap 35 constituting the pressure loss mechanism, the pressure loss energy in the pressure loss mechanism can be recovered as shaft power by the hydro turbine 38. The total efficiency of the multistage centrifugal pump can be improved by effectively utilizing the fluid energy corresponding to the pressure loss in the mechanism.

尚、ハイドロタービン３８のおける羽根は、軸動力を回収するため、ロータ側に単純に遠心方向へ取り付けるだけでは効果は得られないことから、傾けるか又は捩じられるかしてトルクを回収できる羽根角度にすることは言うまでもない。また、ディスク隙間３５及びハイドロタービン３８の構造は、図示例に限定されず、圧損機構と圧損エネルギ回収手段が達成されれば種々の構造変更が可能である。   In addition, since the blade | wing in the hydro turbine 38 collect | recovers shaft power, since it cannot obtain an effect only by attaching it to a rotor side simply to a centrifugal direction, it is the blade | wing which can collect | recover torque by inclining or twisting. Needless to say, the angle. Further, the structures of the disk gap 35 and the hydro turbine 38 are not limited to the illustrated examples, and various structures can be changed as long as the pressure loss mechanism and the pressure loss energy recovery means are achieved.

尚、本発明は上記各実施例に限定されず、本発明の要旨を逸脱しない範囲で各種変更が可能であることはいうまでもない。例えば、パワージェネレータは、電気・動力など種類は問わない。   Needless to say, the present invention is not limited to the above embodiments, and various modifications can be made without departing from the scope of the present invention. For example, the power generator may be of any type such as electricity and power.

本発明に係る流体機械のバイパスエネルギ回収装置は、ポンプ・水車に限らず、圧縮機・タービン等の流体（空気）機械に適用すると好適である。   The bypass energy recovery device for a fluid machine according to the present invention is not limited to a pump and a water turbine, and is preferably applied to a fluid (air) machine such as a compressor and a turbine.

１０ 主軸
１１ 中間ブシュ
１２ 吸込口
１３ 吐出口
１４ 主流路
１４ａ 第１流路
１４ｂ 第２流路
１５ 戻り流路
１６ つり合いブシュ
１７ 戻り流路
１８ つり合い管（バイパス流路）
１９ 内部バイパス用配管（バイパス流路）
２０ パワージェネレータ（圧損機構兼圧損エネルギ回収手段）
２１ａ フランシス型のランナー
２１ｂ プロペラ型のランナー
２２ａ，２２ｂ 水車
２３ａ，２３ｂ 発電機
２５ ハイドロタービン（圧損機構兼圧損エネルギ回収手段）
２５ａ フランシス型のランナー
２６ ギアボックス（変速機）
３０ 主軸
３１ インペラ
３２ バランスディスク
３３ シール部
３４ 高圧側室
３５ ディスク隙間（圧損機構：バイパス流路）
３６ シール部
３７ 羽根
３８ ハイドロタービン（圧損エネルギ回収手段）
３９ 中間ケーシング
４０ 吐出ケーシング
４１ バランス管
４２ 低圧側室
DESCRIPTION OF SYMBOLS 10 Main axis | shaft 11 Intermediate bush 12 Suction port 13 Discharge port 14 Main flow path 14a 1st flow path 14b 2nd flow path 15 Return flow path 16 Balance bush 17 Return flow path 18 Balance pipe (bypass flow path)
19 Internal bypass piping (bypass flow path)
20 Power generator (pressure loss mechanism and pressure loss energy recovery means)
21a Francis type runner 21b Propeller type runner 22a, 22b Water wheel 23a, 23b Generator 25 Hydro turbine (pressure loss mechanism and pressure loss energy recovery means)
25a Francis-type runner 26 Gearbox (transmission)
30 Spindle 31 Impeller 32 Balance disc 33 Sealing part 34 High-pressure side chamber 35 Disc clearance (pressure loss mechanism: bypass flow path)
36 Seal part 37 Blade 38 Hydro turbine (pressure loss energy recovery means)
39 Intermediate casing 40 Discharge casing 41 Balance pipe 42 Low pressure side chamber

Claims (1)

主流路の高圧側から分岐して低圧側に通じるバイパス流路に圧損機構を備えた流体機械において、
前記バイパス流路に、前記圧損機構における圧損エネルギを回収するための圧損エネルギ回収手段を設け、
前記流体機械と前記圧損エネルギ回収手段が別軸であり、
前記圧損エネルギ回収手段は、遠心ポンプにおけるバランスディスクの圧力調整部水路に設置したハイドロタービンである
ことを特徴とする流体機械のバイパスエネルギ回収装置。 In a fluid machine having a pressure loss mechanism in a bypass channel that branches from the high pressure side of the main channel and leads to the low pressure side,
A pressure loss energy recovery means for recovering pressure loss energy in the pressure loss mechanism is provided in the bypass flow path,
The fluid machine and the pressure loss energy recovery means Ri another axial der,
The bypass energy recovery device for a fluid machine, wherein the pressure loss energy recovery means is a hydro turbine installed in a pressure adjustment section water channel of a balance disk in a centrifugal pump .
JP2011011525A 2011-01-24 2011-01-24 Bypass energy recovery device for fluid machinery Expired - Fee Related JP5839803B2 (en)

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JP5839803B2 true JP5839803B2 (en) 2016-01-06

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59192877A (en) * 1983-04-15 1984-11-01 Nippon Steel Corp Water turbine for power retrieval
JPS6291693A (en) * 1985-10-16 1987-04-27 Nikkiso Co Ltd Power recovery-type canning motor pump
IT1234116B (en) * 1989-06-07 1992-04-29 Novax S R L SELF-PRIMING CENTRIFUGAL PUMP.
DE4416497C1 (en) * 1994-05-10 1995-01-12 Gutehoffnungshuette Man Geared multi-shaft turbo-compressor and geared multi-shaft radial expander
JPH10339156A (en) * 1997-06-05 1998-12-22 Sanwa Seiki Co Ltd Power recovering device
DE60215293T2 (en) * 2002-01-17 2007-05-24 Hitachi, Ltd. Energy collector system and associated operating method

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