JP2007064018A - Francis type runner and hydraulic machine - Google Patents

Francis type runner and hydraulic machine Download PDF

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JP2007064018A
JP2007064018A JP2005247909A JP2005247909A JP2007064018A JP 2007064018 A JP2007064018 A JP 2007064018A JP 2005247909 A JP2005247909 A JP 2005247909A JP 2005247909 A JP2005247909 A JP 2005247909A JP 2007064018 A JP2007064018 A JP 2007064018A
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runner
crown
band
francis
line
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JP4768361B2 (en
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Sadao Kurosawa
沢 貞 男 黒
Kaneo Sugishita
下 懷 夫 杉
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Toshiba Corp
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Toshiba Corp
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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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/20—Hydro energy

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Abstract

<P>PROBLEM TO BE SOLVED: To provide a Francis type runner for restraining the occurrence of a hydraulic loss in an undesigned point caused by a secondary flow without increasing a friction loss in a design point. <P>SOLUTION: This Francis type runner is formed by arranging a plurality of runner blades 10 in the peripheral direction between a crown 8 fixed to a rotary shaft and a ring-shaped band 9. At least either one of a band side edge line and a crown side edge line on the rear edge of the runner blades in a meridian cross section, exists on the upstream side more than a line vertically erected to an inner surface of the band or the crown in an intersection between the edge line 10a and the band or an intersection between the edge line 10a and the crown, and is formed in a concave curved shape toward the downstream side. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、フランシス形水車またはポンプ水車等の水力機械に用いられるフランシス形ランナ及び水力機械に関する。   The present invention relates to a Francis type runner and a hydraulic machine that are used in a hydraulic machine such as a Francis type turbine or a pump turbine.

一般に、フランシス形水車またはポンプ水車等の水力機械に用いられるフランシス形ランナは、主軸の軸線を中心に回転可能なクラウンを有し、そのクラウンと離間して設けられたリング状のバンドと上記クラウンの間に、そのクラウン及びバンドを接続するように周方向に複数の板状のランナ羽根が設けられて構成されている。そして、水車運転時にはクラウンとバンドとの間に外方から水を導入し、導入された水の作用により主軸の軸線を中心にフランシス形ランナを回転させ、主軸に連結された発電機を駆動する。   Generally, a Francis-type runner used in a hydraulic machine such as a Francis-type water turbine or a pump-type water wheel has a crown that can rotate around the axis of a main shaft, and a ring-shaped band provided apart from the crown and the above-mentioned crown. In between, a plurality of plate-like runner blades are provided in the circumferential direction so as to connect the crown and the band. When the turbine is in operation, water is introduced from the outside between the crown and the band, and the action of the introduced water rotates the Francis-type runner around the axis of the main shaft to drive the generator connected to the main shaft. .

図３０はフランシス形水車が据え付けられた水力発電所のフランシス形水車近傍の縦断面図であり、発電運転時には、水は図示省略の上池から水圧鉄管を通り、ケーシング１からステーベーン２およびガイドベーン３を通ってランナ４に流れ込み、その水流によってランナ４が回転駆動され、主軸５を介して発電機６が駆動される。一方、ランナ４を駆動した水は吸出し管７を経て図示省略の放水路へと流出する。本運転時にはガイドベーン３の開度を変化させることにより、ランナ４に流入する水量を調整し、発電量を変化させている。なお、フランシス型ランナは、主軸５に固着されたクラウン８と、リング状のバンド９と、上記クラウン８とバンド９とを接続するように配設された複数枚のランナ羽根１０から形成されている。   FIG. 30 is a longitudinal sectional view of the vicinity of a Francis turbine of a hydroelectric power plant in which a Francis turbine is installed. During power generation operation, water passes from an upper pond (not shown) through a hydraulic iron pipe, from a casing 1 to a stay vane 2 and a guide vane. 3 flows into the runner 4, and the runner 4 is rotationally driven by the water flow, and the generator 6 is driven via the main shaft 5. On the other hand, the water that has driven the runner 4 flows out through a suction pipe 7 into a water discharge channel (not shown). During actual operation, the amount of power generation is changed by adjusting the amount of water flowing into the runner 4 by changing the opening of the guide vane 3. The Francis-type runner is formed of a crown 8 fixed to the main shaft 5, a ring-shaped band 9, and a plurality of runner blades 10 disposed so as to connect the crown 8 and the band 9. Yes.

ところで、前述したように運転時には発電量を調整するために、ガイドベーン３の開度を調整し水量を変化させるため、ランナ４内の流れは運転状態により大きく変化する。図３１は水量の違いによるランナ４内の子午面流れの模式を示したものである。即ち、ランナ４の子午面流れは、流れを内周側に押し込もうとする水流の動圧力１１と、流れを外周側に押し出そうとするランナ４の回転による遠心力１２のバランスにより決まるため、設計点（発電効率を最高にしたい点）より水量の小さな運転点では、図３１（ｂ）に示すように、遠心力１２が相対的に大きくなり流れが外周側に偏り、中心部に図３１（ａ）に示す設計点に比較して広い死水領域１３が形成され、設計点（発電効率を最高にしたい点）より水量の大きな運転点では、図３１（ｃ）に示すように、遠心力１２が相対的に小さくなり流れが内周側に偏り、外周側に死水領域１３が形成される。   By the way, as described above, in order to adjust the power generation amount during operation, the opening amount of the guide vane 3 is adjusted and the water amount is changed. Therefore, the flow in the runner 4 varies greatly depending on the operation state. FIG. 31 shows a model of the meridional flow in the runner 4 due to the difference in the amount of water. That is, the meridional flow of the runner 4 is determined by the balance between the dynamic pressure 11 of the water flow that tries to push the flow toward the inner peripheral side and the centrifugal force 12 caused by the rotation of the runner 4 that pushes the flow toward the outer peripheral side. Therefore, at the operating point where the amount of water is smaller than the design point (the point where the power generation efficiency is to be maximized), as shown in FIG. 31 (b), the centrifugal force 12 becomes relatively large and the flow is biased toward the outer peripheral side. Compared to the design point shown in FIG. 31 (a), a wide dead water region 13 is formed, and at an operating point where the amount of water is larger than the design point (a point where power generation efficiency is to be maximized), as shown in FIG. The centrifugal force 12 becomes relatively small, the flow is biased toward the inner periphery, and a dead water region 13 is formed on the outer periphery.

上述した流れの偏りは２次流れと称され、非設計点において、ランナ４内で発生する水力損失の主因となっている。このような、非設計点の２次流れを低減する方法としては、図３２のように、クラウン８とバンド９との間の入口側流路に、クラウン８とバンド９の半径方向長さより短い整流羽根１４をほぼ平行に複数枚ランナ羽根１０から突設する方法が提案されている（例えば特許文献１）。また図３３のようにランナ羽根１０の相互間にランナ羽根よりも翼長が短い中間羽根１５を設ける方法も提案されている（例えば特許文献２）。この様な整流羽根１４や中間羽根１５の整流効果により、設計点より水量の小さな運転点や設計点より水量の大きな運転点では、ランナ４の子午面内流れの偏りが緩和され、２次流れを低減することが出来る。
特開平８−２９６５４４号公報 特開昭５７−１２６５６６号公報 The above-described flow deviation is called a secondary flow, and is a main cause of hydraulic loss occurring in the runner 4 at a non-design point. As a method of reducing the secondary flow at such a non-design point, as shown in FIG. 32, the inlet-side flow path between the crown 8 and the band 9 is shorter than the radial length of the crown 8 and the band 9. There has been proposed a method in which the rectifying blades 14 are protruded from the plurality of runner blades 10 substantially in parallel (for example, Patent Document 1). Further, as shown in FIG. 33, a method of providing an intermediate blade 15 having a blade length shorter than that of the runner blade between the runner blades 10 has been proposed (for example, Patent Document 2). Due to the rectifying effect of the rectifying blades 14 and the intermediate blades 15, the uneven flow in the meridian plane of the runner 4 is mitigated at the operation point where the water amount is smaller than the design point and the operation point where the water amount is larger than the design point. Can be reduced.
JP-A-8-296544 JP-A-57-126666

しかしながら、上述したフランシス形ランナにおいては、２次流れが弱い設計点流れでは、整流羽根１４や中間羽根１５による整流効果が小さく、整流羽根１４や中間羽根１５が摩擦抵抗として強く作用する。このため、非設計点の２次流れ損失は低減されるが、設計点の摩擦損失が増加することが課題であった。   However, in the above-described Francis runner, in the design point flow where the secondary flow is weak, the rectifying effect by the rectifying blades 14 and the intermediate blades 15 is small, and the rectifying blades 14 and the intermediate blades 15 act strongly as frictional resistance. For this reason, the secondary flow loss at the non-design point is reduced, but the problem is that the friction loss at the design point increases.

本発明は上述した課題を解決するためになされたものであり、設計点の摩擦損失を増加させることなく、２次流れに起因した非設計点の水力損失発生を抑制するフランシス形ランナ及び水力機械を提供することを目的とする。   The present invention has been made to solve the above-described problem, and a Francis-type runner and hydraulic machine that suppress the occurrence of hydraulic loss at non-design points caused by the secondary flow without increasing the friction loss at the design points. The purpose is to provide.

本願の第１の発明は、回転軸に固着されたクラウンとリング状のバンドとの間に周方向に複数のランナ羽根が設けられたフランシス形ランナにおいて、子午線断面におけるランナ羽根の後縁のバンド側縁線及びクラウン側縁線の少なくとも一方が、上記縁線とバンドとの交点或いは縁線とクラウンとの交点にてバンド或いはクラウンの内面に対して鉛直に立てた線よりも上流側にあり、且つ下流側に向かって凹曲状に形成されていることを特徴とする。   A first invention of the present application is a Francis-type runner in which a plurality of runner blades are provided in a circumferential direction between a crown fixed to a rotating shaft and a ring-shaped band, and a band at the trailing edge of the runner blade in a meridian section At least one of the side edge line and the crown side edge line is upstream of the intersection of the edge line and the band or the line perpendicular to the inner surface of the band or the crown at the intersection of the edge line and the crown. And it is formed in a concave curved shape toward the downstream side.

また第２の発明は、回転軸に固着されたクラウンとリング状のバンドとの間に周方向に複数のランナ羽根が設けられたフランシス形ランナにおいて、子午線断面におけるランナ羽根の後縁の縁線のバンド付根部位及びクラウン付根部位の少なくとも一方に、下流側に延びるとともに下流側に向かって凹曲状に形成されたフィレットを取付けたことを特徴とする。   A second aspect of the present invention is a Francis-type runner in which a plurality of runner blades are provided in the circumferential direction between a crown fixed to a rotating shaft and a ring-shaped band, and an edge line of a trailing edge of the runner blade in a meridian section At least one of the band root portion and the crown root portion is provided with a fillet that extends downstream and is formed in a concave shape toward the downstream side.

上記構成により、設計点の摩擦損失を増加させることなく、設計点より水量の大きな運転点或いは設計点より水量の少ない運転点の子午面内の２次流れが効果的に低減され、２次流れに起因した非設計点の水力損失発生を抑制することができる。   With the above configuration, the secondary flow in the meridian plane at the operation point having a larger water amount than the design point or the operation point having a smaller water amount than the design point is effectively reduced without increasing the friction loss at the design point, and the secondary flow. It is possible to suppress the occurrence of hydraulic loss at non-design points due to the above.

以下、本発明に係るフランシス形ランナの実施の形態について、図面を参照して説明する。   Embodiments of a Francis runner according to the present invention will be described below with reference to the drawings.

（第１の実施形態）
まず、図１は第１の実施の形態のフランシス形水車ランナの子午断面を示しており、水車ランナは、クラウン８、バンド９、及びランナ羽根１０から形成されている。本実施の形態においては、図１に示されるように、子午断面においてランナ羽根１０の後縁の縁線１０ａのバンド側形状が、縁線１０ａとバンド９との交点Ｐ１ｂにてバンド９に対し鉛直に立てた線１６よりも上流側にあり、且つ下流側に向かって凹曲状に形成されている点を特徴としている。 (First embodiment)
First, FIG. 1 shows a meridional section of the Francis-type turbine runner according to the first embodiment. The turbine runner is formed of a crown 8, a band 9, and a runner blade 10. In the present embodiment, as shown in FIG. 1, the band-side shape of the edge line 10 a of the trailing edge of the runner blade 10 in the meridional section is in relation to the band 9 at the intersection P <b> 1 b between the edge line 10 a and the band 9. It is characterized in that it is on the upstream side of the vertically standing line 16 and is formed in a concave shape toward the downstream side.

このように構成された本実施の形態においては、ランナ羽根後縁近傍に形成されるよどみ点１７で静圧が急激に回復して静圧値が大きくなるため、図２に示されるようにランナ羽根出口のバンド側近傍領域では内周側から外周側へかけて圧力が低下する圧力勾配１８が形成される。この圧力勾配は羽根出口部位のバンド側流れを外周側すなわちバンド側に押し付けるように作用するので、設計点より水量の大きな運転点で発生する外周側の死水領域１３の大きさが低減される。したがって、本実施の形態によれば、図３に示すように、設計点より水量の大きな運転点における子午面内の２次流れが低減され、水力損失発生を抑制することができる。   In the present embodiment configured as described above, the static pressure suddenly recovers at the stagnation point 17 formed in the vicinity of the trailing edge of the runner blade, and the static pressure value increases. Therefore, as shown in FIG. In the region near the band side of the blade outlet, a pressure gradient 18 is formed in which the pressure decreases from the inner peripheral side to the outer peripheral side. Since this pressure gradient acts to press the band side flow at the blade outlet portion toward the outer peripheral side, that is, the band side, the size of the outer dead water region 13 generated at the operating point where the amount of water is larger than the design point is reduced. Therefore, according to the present embodiment, as shown in FIG. 3, the secondary flow in the meridian plane at the operating point where the amount of water is larger than the design point is reduced, and the generation of hydraulic loss can be suppressed.

なお、本実施の形態による発明を効果的に機能させるためは、図４に示すように、回転軸の軸線を含む子午面におけるランナ羽根の後縁の縁線１０ａとバンド９との交点をＰ１ｂ、Ｐ１ｂにてバンド９に対し鉛直に立てた線１６とランナ羽根の後縁の縁線１０ａとの交点をＰ２ｂ、Ｐ１ｂとＰ２ｂとの間に形成される直線Ｌｂの長さをＬＬｂ、直線Ｌｂとランナ羽根の後縁の縁線１０ａとの距離の最大値をｓｂとする時、ｓb／ＬＬｂの値を適正にする必要がある。即ち、ｓb／ＬＬｂの値は０より大きい程、バンド側の子午面内流れを外周側へ押し付ける力１８が強くなるが、図５に示す様に、これに伴い羽根出口中央部付近ではこれとは逆に子午面流れを内周側に押し付ける力１９も強くなる。このため、ｓb／ＬＬｂの値を極度に大きくすると、羽根中央部付近で流れが剥離２０し、２次流れ損失がかえって増大することになる。図６に流れ解析で算定した、ｓb／ＬＬｂと２次流れ損失の関係を示す。本図より、０＜ｓb／ＬＬｂ＜０．１５の領域では、ランナ内の２次流れ損失を低減できていることが分かる。従って、本実施の形態において、
０＜ｓb／ＬＬｂ＜０．１５
と数値限定することで、設計点より水量の大きな運転点の子午面内の２次流れが効果的に低減され、水力損失発生を抑制することができる。 In order for the invention according to the present embodiment to function effectively, as shown in FIG. 4, the intersection of the edge line 10a of the trailing edge of the runner blade on the meridian plane including the axis of the rotation axis and the band 9 is defined as P1b. , The intersection of the line 16 standing perpendicular to the band 9 at P1b and the edge line 10a of the trailing edge of the runner blade is P2b, the length of the straight line Lb formed between P1b and P2b is LLb, and the straight line Lb When the maximum value of the distance between the runner blade and the edge line 10a of the runner blade is sb, the value of sb / LLb needs to be appropriate. That is, as the value of sb / LLb is larger than 0, the force 18 that presses the band-side meridional flow toward the outer peripheral side becomes stronger, but as shown in FIG. On the contrary, the force 19 for pressing the meridional surface flow toward the inner peripheral side also becomes stronger. For this reason, if the value of sb / LLb is extremely increased, the flow is separated 20 near the center of the blade, and the secondary flow loss is increased. FIG. 6 shows the relationship between sb / LLb and secondary flow loss calculated by flow analysis. From this figure, it can be seen that the secondary flow loss in the runner can be reduced in the region of 0 <sb / LLb <0.15. Therefore, in this embodiment,
0 <sb / LLb <0.15
By limiting the numerical values, the secondary flow in the meridian plane at the operating point where the amount of water is larger than the design point is effectively reduced, and the generation of hydraulic loss can be suppressed.

（第２の実施形態）
次に、本発明に係るフランシス形ランナの第２の実施の形態を図７乃至９を用いて説明する。なお、第１の実施の形態と同一の構成には同一の符号を付し、重複する説明は省略する。 (Second Embodiment)
Next, a second embodiment of the Francis-type runner according to the present invention will be described with reference to FIGS. In addition, the same code | symbol is attached | subjected to the structure same as 1st Embodiment, and the overlapping description is abbreviate | omitted.

図７は本発明における第２の実施の形態のフランシス形水車ランナの子午断面を示している。本実施の形態が従来の水車ランナと異なるのは、図７に示されるように、子午断面においてランナ羽根の後縁の縁線１０ａのクラウン側形状が、縁線１０ａとクラウン８の内面との交点Ｐ１ｃにてクラウン８に対し鉛直に立てた線２１よりも上流側にあり、且つその縁線１０ａが下流側に向かって凹曲状に形成されていることである。   FIG. 7 shows a meridional section of the Francis turbine runner according to the second embodiment of the present invention. As shown in FIG. 7, this embodiment differs from the conventional water turbine runner in that the crown side shape of the edge line 10a of the trailing edge of the runner blade in the meridional section is the relationship between the edge line 10a and the inner surface of the crown 8. That is, it is on the upstream side of the line 21 standing vertically with respect to the crown 8 at the intersection P1c, and the edge line 10a is formed in a concave shape toward the downstream side.

このように構成された本実施の形態においては、ランナ羽根後縁近傍に形成されるよどみ点１７で静圧が急激に回復して静圧値が大きくなるため、図８に示されるようにランナ羽根出口クラウン側近傍領域では外周側から内周側へかけて圧力が低下する圧力勾配１９が形成される。本圧力勾配は羽根出口部位のクラウン側流れを内周側に押し付ける様に作用するので、設計点より水量の小さな運転点で発生する内周側の死水領域１３の大きさが低減される。したがって、本実施の形態によれば、設計点より水量の小さな運転点の子午面内の２次流れが低減され、水力損失発生を抑制することができ、図９に示すように、設計点より水量の小さな運転点での水力効率を向上させることができる。   In the present embodiment configured as described above, the static pressure suddenly recovers at the stagnation point 17 formed in the vicinity of the trailing edge of the runner blade, and the static pressure value increases. As shown in FIG. In the vicinity of the blade outlet crown side, a pressure gradient 19 is formed in which the pressure decreases from the outer peripheral side to the inner peripheral side. Since this pressure gradient acts so as to press the crown side flow at the blade outlet portion toward the inner peripheral side, the size of the dead water region 13 on the inner peripheral side generated at the operating point where the amount of water is smaller than the design point is reduced. Therefore, according to the present embodiment, the secondary flow in the meridional plane at the operation point having a smaller water volume than the design point can be reduced, and the generation of hydraulic loss can be suppressed. As shown in FIG. The hydraulic efficiency at the operation point with a small amount of water can be improved.

なお、本実施の形態による発明を効果的に機能させるためは、図１０に示すように、子午面にてランナ羽根の後縁の縁線１０ａとクラウン８との交点をＰ１ｃ、Ｐ１ｃにてクラウン８の内面に対し鉛直に立てた線２１とランナ羽根の後縁の縁線１０ａとの交点をＰ２ｃ、Ｐ１ｃとＰ２ｃとの間に形成される直線Ｌｃの長さをＬＬｃ、直線Ｌｃとランナ羽根の後縁の縁線１０ａとの距離の最大値をｓｃとする時、ｓｃ／ＬＬｃの値を適正にする必要がある。即ち、ｓｃ／ＬＬｃの値は０より大きい程、クラウン側の子午面内流れを内周側へ押し付ける力１９が強くなるが、図１１に示す様に、これに伴い羽根出口中央部付近ではこれとは逆に子午面流れを外周側に押し付ける力１８も強くなる。このため、ｓｃ／ＬＬｃの値を極度に大きくすると、羽根中央部付近で流れが剥離２０し、２次流れ損失がかえって増大することになる。図１２に流れ解析で算定した、ｓｃ／ＬＬｃと２次流れ損失の関係を示す。本図より、０＜ｓｃ／ＬＬｃ＜０．１５の領域では、ランナ内の２次流れ損失を低減できていることが分かる。従って、本実施の形態において
０＜ｓｃ／ＬＬｃ＜０．１５
と数値限定することで、設計点より水量の小さな運転点の子午面内の２次流れが効果的に低減され、水力損失発生を抑制することができる。 In order to make the invention according to the present embodiment function effectively, as shown in FIG. 10, the intersection of the runner blade trailing edge line 10a and the crown 8 on the meridian surface is crowned by P1c and P1c. 8, the intersection of the line 21 standing vertically with respect to the inner surface of the runner 8 and the edge line 10a of the trailing edge of the runner blade is P2c, the length of the straight line Lc formed between P1c and P2c is LLc, the straight line Lc and the runner blade When the maximum value of the distance from the trailing edge line 10a is sc, the value of sc / LLc needs to be appropriate. That is, as the value of sc / LLc is larger than 0, the force 19 that pushes the meridional flow on the crown side toward the inner peripheral side becomes stronger. However, as shown in FIG. On the contrary, the force 18 that presses the meridional surface flow toward the outer peripheral side also increases. For this reason, when the value of sc / LLc is extremely increased, the flow is separated 20 near the center of the blade, and the secondary flow loss is increased. FIG. 12 shows the relationship between sc / LLc and secondary flow loss calculated by flow analysis. From this figure, it can be seen that the secondary flow loss in the runner can be reduced in the region of 0 <sc / LLc <0.15. Therefore, in this embodiment
0 <sc / LLc <0.15
By limiting the numerical values, the secondary flow in the meridian plane at the operating point having a smaller amount of water than the design point is effectively reduced, and the generation of hydraulic loss can be suppressed.

（第３の実施形態）
図１３は本発明の第３の実施の形態のフランシス形水車ランナの子午断面を示している。本実施の形態が従来の水車ランナと異なるのは、図１３に示される様に、子午断面においてランナ羽根１０の後縁の縁線１０ａのクラウン側形状が、縁線１０ａとクラウン８の内面との交点Ｐｃにてクラウンの内面に対し鉛直に立てた線２１よりも上流側にあり、且つ、子午断面においてランナ羽根１０の後縁の縁線１０ａのバンド側形状が、縁線１０ａとバンド９との交点Ｐｂにてバンドに対し鉛直に立てた線１６よりも上流側にあり、しかも上記縁線１０ａが下流方向に向かって凹曲状に形成されていることである。 (Third embodiment)
FIG. 13 shows a meridional section of a Francis turbine runner according to a third embodiment of the present invention. This embodiment is different from the conventional turbine runner as shown in FIG. 13 in that the crown side shape of the edge line 10a of the trailing edge of the runner blade 10 in the meridional section is different from the edge line 10a and the inner surface of the crown 8. The band side shape of the edge line 10a of the trailing edge of the runner blade 10 in the meridional section is the edge line 10a and the band 9 in the meridional section. And the edge line 10a is formed in a concavely curved shape in the downstream direction.

本第３の実施の形態は、第１及び第２の実施の形態を組み合わせたものである。したがって、両者の相乗効果により、非設計点のランナ内の２次流れが低減され、水力損失発生を抑制することができ、図１４に示すように、設計点より水量が大きい運転点及び小さな運転点での水力効率を向上させることができる。   The third embodiment is a combination of the first and second embodiments. Therefore, due to the synergistic effect of the two, the secondary flow in the runner at the non-design point can be reduced and the generation of hydraulic power loss can be suppressed. As shown in FIG. The hydraulic efficiency at a point can be improved.

なお、本実施例による発明を効果的に機能させるためは、図１５に示すように、子午面にてランナ羽根の後縁の縁線１０ａとバンド１０との交点をＰｂ、ランナ羽根の後縁の縁線１０ａとクラウン８との交点Ｐｃ、ＰｂとＰｃとの間に形成される直線Ｌの長さをＬＬ、直線Ｌとランナ羽根の後縁の縁線１０ａとの距離の最大値をｓとする時、ｓ／ＬＬの値を適正にする必要がある。即ち、ｓ／ＬＬの値は０より大きい程、クラウン側の子午面内流れを内周側へ押し付ける力１９とバンド側の子午面流れを外周側へ押し付ける力１８が強くなる。しかしながら、図１６に示す様に、ｓ／ＬＬの値を極度に大きくすると、羽根中央部付近で流れが剥離２０し、２次流れ損失がかえって増大することになる。図１７に流れ解析で算定した、ｓ／ＬＬと２次流れ損失の関係を示す。本図より、０＜ｓ／ＬＬ＜０．１５の領域では、ランナ内の２次流れ損失を低減できていることが分かる。   In order to make the invention according to this embodiment function effectively, as shown in FIG. 15, the intersection of the edge line 10a of the trailing edge of the runner blade and the band 10 is Pb on the meridian surface, and the trailing edge of the runner blade The length of the straight line L formed between the intersections Pc, Pb and Pc of the edge line 10a and the crown 8 is LL, and the maximum distance between the straight line L and the edge line 10a of the trailing edge of the runner blade is s. In this case, the value of s / LL needs to be appropriate. That is, as the value of s / LL is larger than 0, the force 19 for pressing the crown-side meridian flow toward the inner peripheral side and the force 18 for pressing the band-side meridian flow toward the outer peripheral side become stronger. However, as shown in FIG. 16, when the value of s / LL is extremely increased, the flow is separated 20 near the center of the blade, and the secondary flow loss is increased. FIG. 17 shows the relationship between s / LL and secondary flow loss calculated by flow analysis. From this figure, it is understood that the secondary flow loss in the runner can be reduced in the region of 0 <s / LL <0.15.

したがって、本実施の形態において
０＜ｓ／ＬＬ＜０．１５
と数値限定することで、非設計点の子午面内の２次流れがより効果的に低減され、水力損失発生を抑制することができる。 Therefore, in this embodiment
0 <s / LL <0.15
By limiting the numerical values, the secondary flow in the meridian plane at the non-design point can be more effectively reduced, and the generation of hydraulic loss can be suppressed.

（第４の実施形態）
次に、本発明に係るフランシス形ランナの第４の実施の形態を図１８，１９を用いて説明する。なお、第１乃至第３の実施の形態と同一の構成には同一の符号を付し、重複する説明は省略してある。 (Fourth embodiment)
Next, a fourth embodiment of the Francis-type runner according to the present invention will be described with reference to FIGS. In addition, the same code | symbol is attached | subjected to the structure same as 1st thru | or 3rd Embodiment, and the overlapping description is abbreviate | omitted.

図１８は第４の実施の形態のフランシス形水車ランナの子午断面を示している。本実施に形態が従来の水車ランナと異なるのは、図１８に示される様に、子午断面においてランナ羽根１０の後縁の縁線１０ａのバンド付根部位に、下流側にのびるフィレット２２が取付けられていることである。   FIG. 18 shows a meridional section of the Francis turbine runner of the fourth embodiment. The present embodiment is different from the conventional turbine runner in that, as shown in FIG. 18, a fillet 22 extending downstream is attached to the band root portion of the edge line 10a of the trailing edge of the runner blade 10 in the meridional section. It is that.

このように構成された本実施の形態においては、ランナ羽根後縁近傍に形成されるよどみ点１７で静圧が急激に回復して静圧値が大きくなるため、第１の実施の形態と同様に、図１９に示される如くランナ羽根出口バンド側近傍領域では内周側から外周側へかけて圧力が低下する圧力勾配１８が形成される。そして、この圧力勾配は羽根出口部位のバンド側流れを外周側に押し付ける様に作用するので、設計点より水量の大きな運転点で発生する外周側の死水領域１３の大きさが低減される。従って、本実施の形態によれば、設計点より水量の大きな運転点の子午面内の２次流れが低減されるので、水力損失発生を抑制することができ、図２０に示すように、設計点より水量の大きな運転点での水力効率を向上させることができる。   In the present embodiment configured as described above, the static pressure is suddenly recovered at the stagnation point 17 formed in the vicinity of the trailing edge of the runner blade, and the static pressure value is increased. Therefore, as in the first embodiment. In addition, as shown in FIG. 19, in the region near the runner blade outlet band side, a pressure gradient 18 is formed in which the pressure decreases from the inner peripheral side to the outer peripheral side. And since this pressure gradient acts so as to press the band side flow at the blade outlet part to the outer peripheral side, the size of the dead water region 13 on the outer peripheral side generated at the operating point where the amount of water is larger than the design point is reduced. Therefore, according to the present embodiment, since the secondary flow in the meridional plane at the operation point having a larger amount of water than the design point is reduced, it is possible to suppress the occurrence of hydraulic loss, and as shown in FIG. It is possible to improve the hydraulic efficiency at the operation point where the amount of water is larger than the point.

なお、本実施の形態を効果的に機能させるためは、図２１に示すように、子午面におけるランナ羽根の後縁の縁線１０ａとバンド９との交点をＰｂ、ランナ羽根の後縁の縁線１０ａとクラウン８の内面との交点をＰｃ、ＰｂとＰｃとの間に形成される直線の長さをＬＬ、バンド付根部位のフィレット２２の曲率半径をＲｂとする時、Ｒｂ／ＬＬの値を適正にする必要がある。即ち、Ｒｂ／ＬＬの値は０より大きい程、バンド側の子午面内流れを外周側へ押し付ける力１８が強くなる。しかしながら、Ｒｂ／ＬＬの値が極度に小さいと、バンド側の子午面内流れを外周側へ押し付ける力１８が弱く、二次流れ損失低減の明確な効果が現れない。また、Ｒｂ／ＬＬの値を極度に大きくすると、本作用が子午面流路全域に影響を与える様になり、クラウン側の子午面内流れをも外周側に押しやる様に作用し、設計点より水量の大きな運転点の２次流れ損失は減少するが、設計点より水量の小さな運転点の２次流れ損失は増加してしまう。図２２に流れ解析で算定した、Ｒｂ／ＬＬと各運転点での２次流れ損失の関係を示す。本図より、０．０５＜Ｒｂ／ＬＬ＜０．３の領域では、設計点より水量の小さな運転点の２次流れ損失が増加することなく、設計点より水量の大きな運転点の２次流れ損失を低減できていることが分かる。従って、本実施の形態において、
０．０５＜Ｒｂ／ＬＬ＜０．３
と数値限定することで、設計点より水量の大きな運転点の子午面内の２次流れが効果的に低減され、水力損失発生を抑制することができる。 In order to make this embodiment function effectively, as shown in FIG. 21, the intersection of the edge line 10a of the trailing edge of the runner blade and the band 9 on the meridian plane is Pb, and the edge of the trailing edge of the runner blade The value of Rb / LL when the intersection of the line 10a and the inner surface of the crown 8 is Pc, the length of the straight line formed between Pb and Pc is LL, and the radius of curvature of the fillet 22 at the band root is Rb. It is necessary to make it appropriate. That is, as the value of Rb / LL is larger than 0, the force 18 that presses the flow in the meridional surface on the band side toward the outer peripheral side becomes stronger. However, if the value of Rb / LL is extremely small, the force 18 that presses the band-side meridian plane flow toward the outer peripheral side is weak, and a clear effect of reducing the secondary flow loss does not appear. Also, if the value of Rb / LL is extremely increased, this action will affect the entire meridional flow path, and it will act to push the meridional flow on the crown side to the outer peripheral side. Although the secondary flow loss at the operating point with a large amount of water decreases, the secondary flow loss at the operating point with a smaller amount of water than the design point increases. FIG. 22 shows the relationship between Rb / LL and secondary flow loss at each operating point calculated by flow analysis. From this figure, in the region of 0.05 <Rb / LL <0.3, there is no increase in the secondary flow loss at the operation point having a smaller water amount than the design point, and the secondary flow at the operation point having a larger water amount than the design point. It can be seen that the loss can be reduced. Therefore, in this embodiment,
0.05 <Rb / LL <0.3
By limiting the numerical values, the secondary flow in the meridian plane at the operating point where the amount of water is larger than the design point is effectively reduced, and the generation of hydraulic loss can be suppressed.

（第５の実施形態）
次に、本発明に係るフランシス形ランナの第５の実施の形態を図２３、２４を用いて説明する。なお、第１乃至第４の実施の形態と同一の構成には同一の符号を付し、重複する説明は省略する。 (Fifth embodiment)
Next, a fifth embodiment of the Francis runner according to the present invention will be described with reference to FIGS. In addition, the same code | symbol is attached | subjected to the structure same as 1st thru | or 4th Embodiment, and the overlapping description is abbreviate | omitted.

図２３は本第５の実施の形態のフランシス形水車ランナの子午断面を示している。本実施の形態が従来の水車ランナと異なるのは、図２３に示されるように、子午断面においてランナ羽根１０の後縁の縁線１０ａのクラウン付根部位に、下流側にのびるフィレット２３を取付けたことである。   FIG. 23 shows a meridional section of the Francis turbine runner according to the fifth embodiment. As shown in FIG. 23, the present embodiment is different from the conventional turbine runner in that a fillet 23 extending downstream is attached to the crown root portion of the edge line 10a of the trailing edge of the runner blade 10 in the meridional section. That is.

このように構成された本実施の形態においては、ランナ羽根後縁近傍に形成されるよどみ点１７で静圧が急激に回復して静圧値が大きくなるため、第２の実施の形態と同様に、図２４に示される如くランナ羽根出口クラウン側近傍領域では外周側から内周側へかけて圧力が低下する圧力勾配１９が形成される。そして、この圧力勾配は羽根出口部位のクラウン側流れを内周側に押し付ける様に作用するので、設計点より水量の小さな運転点で発生する内周側の死水領域１３の大きさが低減される。従って、本実施の形態によれば、設計点より水量の小さな運転点の子午面内の２次流れが低減されるので、水力損失発生を抑制することができ、図２５に示すように、設計点より水量の小さな運転点での水力効率を向上させることができる。   In the present embodiment configured as described above, the static pressure is suddenly recovered at the stagnation point 17 formed in the vicinity of the trailing edge of the runner blade, and the static pressure value is increased. Therefore, as in the second embodiment. In addition, as shown in FIG. 24, a pressure gradient 19 is formed in the region near the runner blade outlet crown side where the pressure decreases from the outer peripheral side to the inner peripheral side. And since this pressure gradient acts so as to press the crown side flow at the blade outlet part toward the inner peripheral side, the size of the dead water region 13 on the inner peripheral side generated at the operating point where the amount of water is smaller than the design point is reduced. . Therefore, according to the present embodiment, since the secondary flow in the meridian plane at the operation point having a smaller water volume than the design point is reduced, it is possible to suppress the occurrence of hydraulic loss, and as shown in FIG. It is possible to improve the hydraulic efficiency at the operation point where the amount of water is smaller than the point.

なお、本実施の形態を効果的に機能させるためは、図２６に示すように、子午面におけるランナ羽根１０の後縁の縁線１０ａとバンド９との交点をＰｂ、ランナ羽根の後縁の縁線１０ａとクラウン８との交点をＰｃ、ＰｂとＰｃとの間に形成される直線の長さをＬＬ、クラウン付根部位のフィレット２３の曲率半径をＲｃとする時、Ｒｃ／ＬＬの値を適正にする必要がある。即ち、Ｒｃ／ＬＬの値は０より大きい程、クラウン側の子午面内流れを内周側へ押し付ける力１９が強くなる。しかしながら、Ｒｃ／ＬＬの値が極度に小さいと、クラウン側の子午面内流れを内周側へ押し付ける力１９が弱く、二次流れ損失低減の明確な効果が現れない。また、Ｒｃ／ＬＬの値を極度に大きくすると、本作用が子午面流路全域に影響を与える様になり、バンド側の子午面内流れをも内周側に押しやる様に作用し、設計点より水量の小さな運転点の２次流れ損失は減少するが、設計点より水量の大きな運転点の２次流れ損失は増加してしまう。図２７に流れ解析で算定した、Ｒｃ／ＬＬと各運転点での２次流れ損失の関係を示す。本図より、０．０５＜Ｒｃ／ＬＬ＜０．３の領域では、設計点より水量の大きな運転点の２次流れ損失が増加することなく、設計点より水量の小さな運転点の２次流れ損失を低減できていることが分かる。従って、本実施の形態において
０．０５＜Ｒｃ／ＬＬ＜０．３
と数値限定することで、設計点より水量の小さな運転点の子午面内の２次流れが効果的に低減され、水力損失発生を抑制することができる。 In order to make this embodiment function effectively, as shown in FIG. 26, the intersection point between the edge line 10a of the trailing edge of the runner blade 10 and the band 9 on the meridian plane is Pb, and the trailing edge of the runner blade is When the intersection of the edge line 10a and the crown 8 is Pc, the length of the straight line formed between Pb and Pc is LL, and the curvature radius of the fillet 23 at the root portion of the crown is Rc, the value of Rc / LL is It needs to be appropriate. That is, as the value of Rc / LL is larger than 0, the force 19 for pressing the crown side meridional flow toward the inner peripheral side becomes stronger. However, if the value of Rc / LL is extremely small, the force 19 for pressing the crown side meridional flow toward the inner peripheral side is weak, and a clear effect of reducing the secondary flow loss does not appear. Also, if the value of Rc / LL is extremely increased, this action will affect the entire meridional flow path, and the band side meridian flow will also be pushed to the inner circumference side. Although the secondary flow loss at the operation point with a smaller water amount decreases, the secondary flow loss at the operation point with a larger water amount than the design point increases. FIG. 27 shows the relationship between Rc / LL and secondary flow loss at each operating point calculated by flow analysis. From this figure, in the region of 0.05 <Rc / LL <0.3, there is no increase in the secondary flow loss at the operation point having a larger water volume than the design point, and the secondary flow at the operation point having a smaller water volume than the design point. It can be seen that the loss can be reduced. Therefore, in this embodiment
0.05 <Rc / LL <0.3
By limiting the numerical values, the secondary flow in the meridian plane at the operating point having a smaller amount of water than the design point is effectively reduced, and the generation of hydraulic loss can be suppressed.

（第６の実施形態）
次に、本発明に係るフランシス形ランナの第６の実施の形態を図２８を用いて説明する。なお、第１乃至第５の実施の形態と同一の構成には同一の符号を付し、重複する説明は省略する。 (Sixth embodiment)
Next, a sixth embodiment of the Francis-type runner according to the present invention will be described with reference to FIG. In addition, the same code | symbol is attached | subjected to the structure same as 1st thru | or 5th Embodiment, and the overlapping description is abbreviate | omitted.

図２８は本実施の形態のフランシス形水車ランナの子午断面を示している。本実施の形態が従来の水車ランナと異なるのは、図２８に示されるように、子午断面においてランナ羽根１０の後縁の縁線１０ａのクラウン付根部位とバンド付根部位に、下流側に延びるとともに下流側に向かって凹曲状に形成されたフィレット２３、２２を取付けたことことである。   FIG. 28 shows a meridional section of the Francis turbine runner of the present embodiment. As shown in FIG. 28, the present embodiment is different from the conventional water turbine runner in that it extends downstream from the crown root portion and the band root portion of the edge line 10a of the trailing edge of the runner blade 10 in the meridian section. That is, the fillets 23 and 22 formed in a concave shape toward the downstream side are attached.

本実施の形態は、第４及び第５の実施の形態を組み合わせたものである。したがって、両者の相乗効果により、非設計点のランナ内の２次流れがより効果的に低減され、水力損失発生を抑制することができ、図２９に示すように、設計点より水量の小さな運転点及び大きな設計点での水力効率を向上させることができる。   This embodiment is a combination of the fourth and fifth embodiments. Therefore, due to the synergistic effect of the two, the secondary flow in the runner at the non-design point can be more effectively reduced and the generation of hydraulic power loss can be suppressed. As shown in FIG. The hydraulic efficiency at the point and the large design point can be improved.

本発明における第１の実施の形態のフランシス形水車ランナの子午断面図。The meridional sectional view of the Francis type turbine runner according to the first embodiment of the present invention. 第１の実施の形態のフランシス形水車ランナの内部流れ模式図。The internal flow schematic diagram of the Francis type turbine runner of a 1st embodiment. 第１の実施の形態における水力効率の変化を示す図。The figure which shows the change of the hydraulic efficiency in 1st Embodiment. 第１の実施の形態における各部寸法の説明図。Explanatory drawing of each part dimension in 1st Embodiment. 第１の実施の形態のフランシス形水車ランナの内部流れ模式図。The internal flow schematic diagram of the Francis type turbine runner of a 1st embodiment. 第１の実施の形態のフランシス形水車ランナのｓｂ／ＬＬｂと２次流れ損失相関図。The sb / LLb and secondary flow loss correlation diagram of the Francis type turbine runner of a 1st embodiment. 第２の実施の形態のフランシス形水車ランナの子午断面図The meridional section of the Francis turbine runner of the second embodiment 第２の実施の形態のフランシス形水車ランナの内部流れ模式図Schematic diagram of the internal flow of the Francis turbine runner of the second embodiment 第２の実施の形態における水力効率の変化を示す図。The figure which shows the change of the hydraulic efficiency in 2nd Embodiment. 第２の実施の形態における各部寸法の説明図。Explanatory drawing of each part dimension in 2nd Embodiment. 第２の実施の形態のフランシス形水車ランナの内部流れ模式図Schematic diagram of the internal flow of the Francis turbine runner of the second embodiment 第２の実施の形態のフランシス形水車ランナのｓｃ／ＬＬｃと２次流れ損失相関図Sc / LLc and secondary flow loss correlation diagram of Francis turbine runner of the second embodiment 第３の実施の形態のフランシス形水車ランナの子午断面図The meridional section of the Francis turbine runner of the third embodiment 第３の実施の形態における水力効率の変化を示す図。The figure which shows the change of the hydraulic efficiency in 3rd Embodiment. 第３の実施の形態における各部寸法の説明図。Explanatory drawing of each part dimension in 3rd Embodiment. 第３の実施の形態のフランシス形水車ランナの内部流れ模式図Schematic diagram of the internal flow of the Francis turbine runner of the third embodiment 第３の実施の形態のフランシス形水車ランナのｓ／ＬＬと２次流れ損失相関図S / LL and secondary flow loss correlation diagram of Francis turbine runner of third embodiment 第４の実施の形態のフランシス形水車ランナの子午断面図The meridional section of the Francis turbine runner of the fourth embodiment 第４の実施の形態のフランシス形水車ランナの内部流れ模式図Schematic diagram of the internal flow of the Francis turbine runner of the fourth embodiment 第４の実施の形態における水力効率の変化を示す図。The figure which shows the change of the hydraulic efficiency in 4th Embodiment. 第４の実施の形態における各部寸法の説明図。Explanatory drawing of each part dimension in 4th Embodiment. 第４の実施の形態のフランシス形水車ランナのＲｂ／ＬＬと２次流れ損失相関図Rb / LL and secondary flow loss correlation diagram of Francis turbine runner according to the fourth embodiment 第５の実施の形態のフランシス形水車ランナの子午断面図Meridian section of Francis turbine runner of fifth embodiment 第５の実施の形態のフランシス形水車ランナの内部流れ模式図Schematic diagram of internal flow of Francis turbine runner of fifth embodiment 第５の実施の形態における水力効率の変化を示す図。The figure which shows the change of the hydraulic efficiency in 5th Embodiment. 第５の実施の形態における各部寸法の説明図。Explanatory drawing of each part dimension in 5th Embodiment. 第５の実施の形態のフランシス形水車ランナのＲｃ／ＬＬと２次流れ損失相関図Rc / LL and secondary flow loss correlation diagram of Francis turbine runner of fifth embodiment 第６の実施の形態のフランシス形水車ランナの子午断面図。The meridional sectional view of the Francis type turbine runner of the sixth embodiment. 第６の実施の形態における水力効率の変化を示す図。The figure which shows the change of the hydraulic efficiency in 6th Embodiment. 従来のフランシス形水車ランナが据え付けられた水力発電所の縦断面図。The longitudinal cross-sectional view of the hydroelectric power plant in which the conventional Francis type turbine runner was installed. （ａ）、（ｂ）、（ｃ）は、それぞれ水量の違いによるランナ内の子午面内流れ模式図。(A), (b), (c) is a schematic view of the flow in the meridional plane in the runner due to the difference in water amount. 従来の２次流れ低減技術を示す図。The figure which shows the conventional secondary flow reduction technique. 従来の２次流れ低減技術を示す図。The figure which shows the conventional secondary flow reduction technique.

符号の説明Explanation of symbols

１ ケーシング
３ ガイドベーン
４ ランナ
５ 吸出し管
８ クラウン
９ バンド
１０ 羽根
１０ａ 羽根後縁の縁線
１３ 死水領域
１６ バンド面に対し鉛直に立てた線
１７ 静圧が急激に回復するよどみ点領域
１８ 圧力勾配により外周側に作用する流体力
１９ 圧力勾配により内周側に作用する流体力
２１ クラウン面に対し鉛直に立てた線
２２ フィレット DESCRIPTION OF SYMBOLS 1 Casing 3 Guide vane 4 Runner 5 Suction pipe 8 Crown 9 Band 10 Blade 10a Blade trailing edge edge line 13 Dead water area 16 Line standing perpendicular to the band surface 17 Stagnation point area 18 where static pressure recovers rapidly 18 Pressure gradient The fluid force 19 acting on the outer peripheral side by the fluid force 21 acting on the inner peripheral side due to the pressure gradient The line 22 standing perpendicular to the crown surface 22 Fillet

Claims (5)

回転軸に固着されたクラウンとリング状のバンドとの間に周方向に複数のランナ羽根が設けられたフランシス形ランナにおいて、子午断面におけるランナ羽根の後縁のバンド側縁線及びクラウン側縁線の少なくとも一方が、上記縁線とバンドとの交点或いは縁線とクラウンとの交点にてバンド或いはクラウンの内面に対して鉛直に立てた線よりも上流側にあり、且つ下流側に向かって凹曲状に形成されていることを特徴とする、フランシス形ランナ。   In a Francis type runner in which a plurality of runner blades are provided in the circumferential direction between a crown fixed to a rotating shaft and a ring-shaped band, a band side edge line and a crown side edge line of the trailing edge of the runner blade in the meridional section Is at the upstream side of the line perpendicular to the band or the inner surface of the band or the crown at the intersection of the edge line and the band or at the intersection of the edge line and the crown, and concave toward the downstream side. Francis-type runner characterized by being formed in a curved shape. 上記ランナ羽根後縁の縁線とバンド或いはクラウンとの交点をＰ１ｂまたはＰ１ｃ、Ｐ１ｂまたはＰ１ｃにてバンド或いはクラウンの内面に対して鉛直に立てた線とランナ羽根後縁の縁線との交点をＰ２ｂまたはＰ２ｃ、Ｐ１ｂとＰ２ｂとの間に形成される直線をＬＬｂ、Ｐ１ｃとＰ２ｃとの間に形成される直線をＬＬｃ、直線ＬＬｂまたはＬＬｃとランナ羽根後縁の縁線との距離の最大値をｓｂまたはｓｃとすると、
０＜ｓｂ／ＬＬｂ＜０．１５
または ０＜ｓｃ／ＬＬｃ＜０．１５
を満たすことを特徴とする、請求項１記載のフランシス形ランナ。 The intersection point between the edge line of the runner blade trailing edge and the band or crown is defined as the intersection point of the line perpendicular to the inner surface of the band or crown at P1b or P1c, P1b or P1c and the edge line of the runner blade trailing edge. P2b or P2c, the straight line formed between P1b and P2b is LLb, the straight line formed between P1c and P2c is LLc, and the maximum distance between the straight line LLb or LLc and the edge line of the runner blade trailing edge Is sb or sc
0 <sb / LLb <0.15
Or 0 <sc / LLc <0.15
The Francis runner according to claim 1, wherein: 回転軸に固着されたクラウンとリング状のバンドとの間に周方向に複数のランナ羽根が設けられたフランシス形ランナにおいて、子午断面におけるランナ羽根の後縁の縁線のバンド付根部位及びクラウン付根部位の少なくとも一方に、下流側に延びるとともに下流側に向かって凹曲状に形成されたフィレットを取付けたことを特徴とするフランシス形ランナ。   In a Francis-type runner in which a plurality of runner blades are provided in a circumferential direction between a crown fixed to a rotating shaft and a ring-shaped band, a band root portion and a crown root of an edge line of a trailing edge of the runner blade in a meridional section A Francis-type runner characterized in that a fillet extending downstream and formed concavely toward the downstream side is attached to at least one of the parts. 子午線断面におけるランナ羽根の後縁の縁線とバンドとの交点をＰｂ、ランナ羽根の後縁の縁線とクラウンとの交点をＰｃ、ＰｂとＰｃとの間に形成される直線の長さをＬＬ、バンド付根部位或いはクラウン付根部位のフィレットの曲率半径をＲｂまたはＲｃとすると、
０．０５ ＜ Ｒｂ／ＬＬ ＜ ０．３
または ０．０５ ＜ Ｒｃ／ＬＬ ＜ ０．３
を満たすことを特徴とする、請求項３記載のフランシス形ランナ。 In the meridian section, the intersection of the trailing edge of the runner blade and the band is Pb, the intersection of the trailing edge of the runner blade and the crown is Pc, and the length of the straight line formed between Pb and Pc is LL, where the radius of curvature of the fillet of the band root part or crown root part is Rb or Rc,
0.05 <Rb / LL <0.3
Or 0.05 <Rc / LL <0.3
The Francis-type runner according to claim 3, wherein: 請求項１乃至４のいずれかに記載のフランシス形ランナを備えた水力機械。   The hydraulic machine provided with the Francis type runner in any one of Claims 1 thru | or 4.
JP2005247909A 2005-08-29 2005-08-29 Francis type runner and hydraulic machine Expired - Fee Related JP4768361B2 (en)

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KR20170056517A (en) * 2014-07-23 2017-05-23 안드리츠 하이드로 엘티디. Francis turbine with short blade and short band
US10087906B2 (en) 2013-08-20 2018-10-02 Kabushiki Kaisha Toshiba Hydraulic turbine and pipe
EP3683437A1 (en) * 2019-01-18 2020-07-22 GE Renewable Technologies Hydroturbine runner blade local extension to avoid cavitation erosion
CN112177972A (en) * 2019-07-02 2021-01-05 戴博水泵股份有限公司 Impeller for a centrifugal pump and pump having such an impeller

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JPH06229365A (en) * 1993-02-03 1994-08-16 Toshiba Corp Inspection device for water turbine runner
JPH1030544A (en) * 1996-07-18 1998-02-03 Toshiba Corp Fluid machine
JP2005009321A (en) * 2003-06-16 2005-01-13 Toshiba Corp Francis type runner

Cited By (18)

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Publication number Priority date Publication date Assignee Title
US20100086394A1 (en) * 2008-10-03 2010-04-08 Kabushiki Kaisha Toshiba Hydraulic machine
US9181957B2 (en) * 2008-10-03 2015-11-10 Yasuyuki Enomoto Hydraulic machine
WO2012143518A1 (en) * 2011-04-20 2012-10-26 Alstom Hydro France Runner for a hydraulic machine, hydraulic machine provided with such a runner, and power-conversion equipment including such a hydraulic machine
FR2974394A1 (en) * 2011-04-20 2012-10-26 Alstom Hydro France WHEEL FOR HYDRAULIC MACHINE, HYDRAULIC MACHINE EQUIPPED WITH SUCH WHEEL AND ENERGY CONVERSION INSTALLATION COMPRISING SUCH A HYDRAULIC MACHINE
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CN107076101A (en) * 2014-07-23 2017-08-18 安德里兹水利有限公司 Francis turbine with short blade and short lower ring
JP2017520720A (en) * 2014-07-23 2017-07-27 アンドリッツ ハイドロ リミテッド Francis turbine with short blades and short bands
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EP3683437A1 (en) * 2019-01-18 2020-07-22 GE Renewable Technologies Hydroturbine runner blade local extension to avoid cavitation erosion
WO2020148415A1 (en) * 2019-01-18 2020-07-23 Ge Renewable Technologies Hydroturbine runner blade local extension to avoid cavitation erosion
CN113474549A (en) * 2019-01-18 2021-10-01 通用电气再生能源技术公司 Local extension of water turbine runner blades to avoid cavitation erosion
CN113474549B (en) * 2019-01-18 2023-08-22 通用电气再生能源技术公司 Hydraulic turbine and method for improving performance thereof
CN112177972A (en) * 2019-07-02 2021-01-05 戴博水泵股份有限公司 Impeller for a centrifugal pump and pump having such an impeller

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