JP3949663B2 - Centrifugal impeller - Google Patents

Centrifugal impeller Download PDF

Info

Publication number
JP3949663B2
JP3949663B2 JP2004021783A JP2004021783A JP3949663B2 JP 3949663 B2 JP3949663 B2 JP 3949663B2 JP 2004021783 A JP2004021783 A JP 2004021783A JP 2004021783 A JP2004021783 A JP 2004021783A JP 3949663 B2 JP3949663 B2 JP 3949663B2
Authority
JP
Japan
Prior art keywords
impeller
centrifugal
blade
centrifugal impeller
rear surface
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.)
Expired - Lifetime
Application number
JP2004021783A
Other languages
Japanese (ja)
Other versions
JP2004353655A (en
Inventor
銀春 曹
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sanso Electric Co Ltd
Original Assignee
Sanso Electric Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sanso Electric Co Ltd filed Critical Sanso Electric Co Ltd
Priority to JP2004021783A priority Critical patent/JP3949663B2/en
Publication of JP2004353655A publication Critical patent/JP2004353655A/en
Priority to CNB2005100070081A priority patent/CN100434723C/en
Application granted granted Critical
Publication of JP3949663B2 publication Critical patent/JP3949663B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Landscapes

  • Structures Of Non-Positive Displacement Pumps (AREA)

Description

本発明は、遠心ポンプなどの遠心流体機械に有する遠心羽根車の構造に関し、特に遠心ポンプの遠心羽根車の構造に関する。   The present invention relates to a structure of a centrifugal impeller included in a centrifugal fluid machine such as a centrifugal pump, and more particularly to a structure of a centrifugal impeller of a centrifugal pump.

図１に示す遠心流体機械である遠心ポンプの遠心羽根車１では、図４および図５に示すように、流体を羽根間流路１０に流れる流体をスムーズに流すことができ、かつ、遠心羽根車１の効率を高効率なものに実現するために、羽根４への無衝突流入条件を確保するために羽根入口角１６を入口流れ角１７に合わせることおよび羽根間流路１０における衝突による損失の発生を少なくすることが重要である。   In the centrifugal impeller 1 of the centrifugal pump that is the centrifugal fluid machine shown in FIG. 1, as shown in FIGS. 4 and 5, the fluid flowing through the inter-blade channel 10 can flow smoothly, and the centrifugal blade In order to achieve high efficiency of the vehicle 1, the blade inlet angle 16 is matched with the inlet flow angle 17 in order to ensure the collision-free inflow condition to the blade 4, and the loss due to the collision in the passage 10 between the blades. It is important to reduce the occurrence of this.

一方、普通の遠心ポンプはその性能上の考慮から、遠心羽根車１の羽根入口１１の半径を羽根車ハブ３側から羽根車後面シュラウド５側に向かって徐々に大きくする必要がある。そこで、遠心羽根車１の羽根入口角１６を羽根車ハブ３側から羽根車後面シュラウド５側に向かって徐々に小さくするように遠心羽根車１を設計しなければならない。その結果、図３と図４に示すように、現状では遠心羽根車１の羽根圧力面６と羽根負圧面７とが羽根高さ１８の方向に捻られている三次元曲面形状の羽根４を用いたものが多く使用されている。   On the other hand, from the viewpoint of performance, an ordinary centrifugal pump needs to gradually increase the radius of the blade inlet 11 of the centrifugal impeller 1 from the impeller hub 3 side toward the impeller rear surface shroud 5 side. Therefore, the centrifugal impeller 1 must be designed so that the blade inlet angle 16 of the centrifugal impeller 1 gradually decreases from the impeller hub 3 side toward the impeller rear surface shroud 5 side. As a result, as shown in FIGS. 3 and 4, the blade 4 having a three-dimensional curved surface in which the blade pressure surface 6 and the blade negative pressure surface 7 of the centrifugal impeller 1 are twisted in the direction of the blade height 18 at present. Many used are used.

しかし、このような三次元曲面形状の羽根４を持つ遠心羽根車１を量産する時、特に樹脂製羽根車を量産する場合に、遠心羽根車１の羽根４が羽根高さ１８の方向に捻られているため、遠心羽根車１を量産用の金型から取り出しにくい。それで、三次元曲面形状の羽根４を持つ遠心羽根車１の量産は、金型が複雑になっている上に、生産効率も悪くなっているのが現状である。   However, when mass-producing the centrifugal impeller 1 having the blades 4 having such a three-dimensional curved surface, especially when mass-producing the resin impeller, the blades 4 of the centrifugal impeller 1 are twisted in the direction of the blade height 18. Therefore, it is difficult to take out the centrifugal impeller 1 from the mold for mass production. Therefore, in the mass production of the centrifugal impeller 1 having the blades 4 having a three-dimensional curved surface shape, the mold is complicated and the production efficiency is deteriorated.

一方、従来の遠心羽根車１の場合、特に樹脂製羽根車の場合は、遠心羽根車１が量産用の金型から取り出しやすくするために、図５に示すように、遠心羽根車１の羽根圧力面６が羽根負圧面７と共に二次元曲面形状になっているものが殆どである。しかし、このように羽根４の形状を二次元曲面形状にすると、遠心羽根車１の羽根入口角１６は入口流れ角１７と合わなくなり、羽根４への大きな衝突損失が生じることとなり、羽根間流路１０における損失も大きな損失となって発生すると考えられている。このために二次元曲面形状をした羽根４からなる遠心羽根車１において高効率化を実現することは難しかった。   On the other hand, in the case of the conventional centrifugal impeller 1, particularly in the case of a resin impeller, in order to make the centrifugal impeller 1 easy to take out from a mold for mass production, as shown in FIG. In most cases, the pressure surface 6 and the blade suction surface 7 have a two-dimensional curved surface shape. However, if the shape of the blades 4 is made into a two-dimensional curved surface shape in this way, the blade inlet angle 16 of the centrifugal impeller 1 will not match the inlet flow angle 17 and a large collision loss to the blades 4 will occur. It is considered that the loss in the road 10 also occurs as a large loss. For this reason, it has been difficult to achieve high efficiency in the centrifugal impeller 1 including the blades 4 having a two-dimensional curved surface shape.

特願２００２−１１９７６４（平成１４年４月２２日出願）Japanese Patent Application No. 2002-119964 (filed on April 22, 2002) 「ターボ機械」、第３１巻、１０号（２００３年１０月号）、p２２〜２８、日本工業出版（株）“Turbo Machine”, Vol. 31, No. 10 (October 2003), p22-28, Nihon Kogyo Publishing Co., Ltd.

本発明が解決しようとする課題は、遠心羽根車の高効率化を実現しながら、遠心羽根車の量産用の金型を簡易化して生産効率を高め、さらに低騒音ポンプの実現も合わせて図ることができる羽根車を提供することである。   The problem to be solved by the present invention is to increase the production efficiency by simplifying the mold for mass production of the centrifugal impeller while realizing the high efficiency of the centrifugal impeller, and also to realize the low noise pump. It is to provide an impeller that can.

本発明では、遠心羽根車１の羽根間流路１０に流れる流体をスムーズに流せて、遠心羽根車１の高効率化を実現するため、遠心羽根車１の羽根入口１１における流れの羽根４への無衝突流入が非常に重要である。
そこで、上記の課題を解決するための本発明の手段は、遠心羽根車１を有する遠心流体機械、例えば遠心ポンプにおいて、遠心羽根車１の羽根圧力面６を二次元曲面形状とし、羽根負圧面７を三次元曲面形状とし、羽根車ハブ３側の羽根厚み１９を羽根車後面シュラウド５側の羽根厚み１９より厚くし、かつ、羽根厚み１９を羽根車ハブ３側から羽根車後面シュラウド５側に徐々に薄くしたことにより、遠心羽根車１の羽根入口角１６を羽根車ハブ３側から羽根車後面シュラウド５側に向かって徐々に小さくしたことを特徴とする遠心羽根車１である。 In the present invention, the fluid flowing through the inter-blade channel 10 of the centrifugal impeller 1 can be smoothly flowed to achieve high efficiency of the centrifugal impeller 1, so that the flow blade 4 at the blade inlet 11 of the centrifugal impeller 1 can be realized. The collision-free inflow is very important.
Therefore, the means of the present invention for solving the above-mentioned problem is that in a centrifugal fluid machine having a centrifugal impeller 1, for example, a centrifugal pump, the blade pressure surface 6 of the centrifugal impeller 1 has a two-dimensional curved surface shape, and the blade negative pressure surface. 7 is a three-dimensional curved surface, the blade thickness 19 on the impeller hub 3 side is made thicker than the blade thickness 19 on the impeller rear surface shroud 5 side, and the blade thickness 19 is changed from the impeller hub 3 side to the impeller rear surface shroud 5 side. The centrifugal impeller 1 is characterized in that the blade inlet angle 16 of the centrifugal impeller 1 is gradually decreased from the impeller hub 3 side toward the impeller rear surface shroud 5 side.

さらに、遠心羽根車１は、羽根車後面シュラウド５側の羽根入口半径をｒ１ｓとし、羽根車後面シュラウド５側の羽根出口半径をｒ２ｓとするとき、羽根半径ｒがｒ１ｓ＋（ｒ２ｓ−ｒ１ｓ）２／３より小さい羽根４の部分において、羽根厚み１９を羽根車ハブ３側から羽根車後面シュラウド５側に徐々に薄くしたことにより、遠心羽根車１の羽根入口角１６を羽根車ハブ３側から羽根車後面シュラウド５側に向かって徐々に小さくしたことを特徴とする上記の手段の遠心羽根車１である。   Further, the centrifugal impeller 1 has a blade radius r of r1s + (r2s−r1s) 2 / r, where r1s is a blade inlet radius on the rear wheel shroud 5 side and r2s is a blade outlet radius on the rear wheel shroud 5 side. In the portion of the blade 4 smaller than 3, the blade thickness 19 is gradually reduced from the impeller hub 3 side to the impeller rear surface shroud 5 side, so that the blade inlet angle 16 of the centrifugal impeller 1 is changed from the impeller hub 3 side to the impeller hub 3 side. The centrifugal impeller 1 of the above-described means is characterized in that it is gradually reduced toward the vehicle rear surface shroud 5 side.

さらに、遠心羽根車１は、羽根車ハブ３のみを有し羽根車後面シュラウド５を無くしたセミオープン遠心羽根車、又は羽根車ハブ３を短くし、さらに羽根車後面シュラウド５を無くしたフルオープン遠心羽根車からなることを特徴とする上記のいずれかの手段の遠心羽根車１である。   Further, the centrifugal impeller 1 is a semi-open centrifugal impeller having only the impeller hub 3 and having no impeller rear surface shroud 5 or a short opening of the impeller hub 3 and further fully opening having no impeller rear shroud 5. The centrifugal impeller 1 according to any one of the above-mentioned means is characterized by comprising a centrifugal impeller.

上記の手段の構成とすることにより、遠心羽根車１の高効率化および低騒音化が実現でき、しかも遠心羽根車１の形状が金型から取り出しやすい形状になっているため、遠心羽根車１を量産する金型も簡易化でき、遠心羽根車１の生産効率を一層に高めることができる。   With the configuration of the above means, the centrifugal impeller 1 can achieve high efficiency and low noise, and the centrifugal impeller 1 has a shape that can be easily taken out from the mold. Therefore, it is possible to simplify the mold for mass production of the centrifugal impeller 1 and further increase the production efficiency of the centrifugal impeller 1.

以上に説明したように、従来の羽根圧力面および羽根負圧面の形状を共に三次元曲面形状とした羽根車をもつ遠心流体機械と比べ、本発明の羽根圧力面の形状を二次元曲面形状とし、羽根負圧面を三次元曲面形状とした羽根を有する遠心羽根車を採用することによって、本発明の遠心羽根車は遠心流体機械の全効率を低下することなく、しかも量産用の金型から取り出しやすい形状となっており、このため羽根車の量産用の金型形状を簡易化することができ、遠心羽根車を量産する生産効率も高めることができるなど、本発明は優れた効果を奏する。   As described above, the blade pressure surface of the present invention has a two-dimensional curved surface shape as compared with a centrifugal fluid machine having an impeller in which both the blade pressure surface and the blade suction surface have a three-dimensional curved surface shape. By adopting a centrifugal impeller having blades whose vane suction surface has a three-dimensional curved surface, the centrifugal impeller of the present invention can be taken out from a mold for mass production without reducing the overall efficiency of the centrifugal fluid machine. The present invention has an excellent effect that the shape of the mold for mass production of the impeller can be simplified, and the production efficiency for mass production of the centrifugal impeller can be increased.

本発明を実施するための最良の形態を添付の図面を参照して説明する。添付の図面において、図１は遠心羽根車１を有する遠心ポンプの断面図である。図２は本発明の一実施の形態の遠心羽根車１の構造を説明する模式図である。図３は他の実施の形態の遠心羽根車の一部断面図である。図４は羽根入口速度を示す三角形を説明する図である。図５は従来の三次元曲面形状の遠心羽根車１の構造を説明する模式図である。図６は従来の二次元曲面形状の遠心羽根車１の構造を説明する模式図である。図７は本発明の遠心羽根車１を持つ遠心ポンプと従来の三次元曲面形状の遠心羽根車１を持つ遠心ポンプの性能を比較するグラフで、揚水量Ｑに対する全揚程Ｈとポンプの入力の関係を示すグラフである。図８は本発明の遠心羽根車１を持つ遠心ポンプと従来の三次元曲面形状の遠心羽根車１を持つ遠心ポンプの性能を比較するグラフで、揚水量Ｑに対するポンプ効率の関係を示すグラフである。図９は本発明の遠心羽根車１を持つ遠心ポンプと従来の三次元曲面形状の遠心羽根車１を持つ遠心ポンプの騒音を比較して示すグラフである。   The best mode for carrying out the present invention will be described with reference to the accompanying drawings. In the accompanying drawings, FIG. 1 is a sectional view of a centrifugal pump having a centrifugal impeller 1. FIG. 2 is a schematic diagram for explaining the structure of the centrifugal impeller 1 according to the embodiment of the present invention. FIG. 3 is a partial cross-sectional view of a centrifugal impeller according to another embodiment. FIG. 4 is a diagram for explaining a triangle indicating the blade inlet velocity. FIG. 5 is a schematic diagram for explaining the structure of a conventional centrifugal impeller 1 having a three-dimensional curved surface shape. FIG. 6 is a schematic diagram for explaining the structure of a conventional centrifugal impeller 1 having a two-dimensional curved surface shape. FIG. 7 is a graph comparing the performance of the centrifugal pump having the centrifugal impeller 1 of the present invention and the conventional centrifugal pump having the centrifugal impeller 1 having a three-dimensional curved surface. It is a graph which shows a relationship. FIG. 8 is a graph comparing the performance of a centrifugal pump having the centrifugal impeller 1 of the present invention and a centrifugal pump having a conventional centrifugal impeller 1 having a three-dimensional curved shape. is there. FIG. 9 is a graph showing a comparison of noise between a centrifugal pump having the centrifugal impeller 1 of the present invention and a conventional centrifugal pump having a three-dimensional curved centrifugal impeller 1.

本発明の遠心流体機械の一実施の形態である遠心ポンプは、図１に示すように、汲み上げる液体を吸込むポンプ吸込口８と液体を吐出するポンプ吐出口９をケーシング２０に有し、ケーシング２０内に渦巻室２を有する。この渦巻室２内にはモータにより回転される遠心羽根車１が配設されている。遠心羽根車１の回転により渦巻室２に羽根入口１１から吸い込まれた液体は渦巻室２の周辺部の羽根出口１２からポンプ吐出口９を通じて吐出される。この遠心ポンプは、図２に示すように、この遠心羽根車１の羽根入口１１は羽根入口ハブ側半径１３と羽根入口中間部半径１４と羽根入口シュラウド側半径１５の大きさを有し、羽根４の羽根圧力面６は二次元曲面形状からなり、羽根４の羽根負圧面７は三次元曲面形状からなっている。さらに羽根車ハブ３側の羽根厚み１９は羽根車後面シュラウド５側の羽根厚み１９に比して厚く形成されており、かつ、この羽根厚み１９は羽根車ハブ３側から羽根車後面シュラウド５側に向かって徐々に薄くなっている。このようにすることで、遠心羽根車１の羽根入口角１６は羽根車ハブ３側から羽根車後面シュラウド５側に向かって徐々に小さく形成される。   As shown in FIG. 1, the centrifugal pump according to the embodiment of the centrifugal fluid machine of the present invention has a pump suction port 8 for sucking up the liquid to be pumped and a pump discharge port 9 for discharging the liquid in the casing 20. A spiral chamber 2 is provided inside. A centrifugal impeller 1 that is rotated by a motor is disposed in the spiral chamber 2. The liquid sucked into the spiral chamber 2 from the blade inlet 11 by the rotation of the centrifugal impeller 1 is discharged from the blade outlet 12 around the spiral chamber 2 through the pump discharge port 9. In this centrifugal pump, as shown in FIG. 2, the blade inlet 11 of the centrifugal impeller 1 has a blade inlet hub side radius 13, a blade inlet middle radius 14 and a blade inlet shroud side radius 15. The blade pressure surface 6 of 4 has a two-dimensional curved surface shape, and the blade negative pressure surface 7 of the blade 4 has a three-dimensional curved surface shape. Further, the blade thickness 19 on the impeller hub 3 side is formed thicker than the blade thickness 19 on the impeller rear surface shroud 5 side, and this blade thickness 19 is from the impeller hub 3 side to the impeller rear surface shroud 5 side. It is getting thinner gradually. By doing in this way, the blade | wing inlet angle 16 of the centrifugal impeller 1 is formed gradually small toward the impeller rear surface shroud 5 side from the impeller hub 3 side.

さらに、本発明の遠心流体機械の他の実施の形態である遠心ポンプは、羽根車後面シュラウド５側の羽根入口１１の半径１５をｒ１ｓとし、羽根車後面シュラウド５側の羽根出口１２の半径すなわち羽根出口後面シュラウド側半径２１をｒ２ｓとするとき、羽根半径ｒがｒ１ｓ＋（ｒ２ｓ−ｒ１ｓ）２／３より小さい羽根４の部分において、羽根厚み１９を羽根車ハブ３側から羽根車後面シュラウド５側に徐々に薄くしたものである。このようにすることで、さらに遠心羽根車１の羽根入口角１６は羽根車ハブ３側から羽根車後面シュラウド５側に向かって徐々に小さく形成されることとなる。   Furthermore, in the centrifugal pump according to another embodiment of the centrifugal fluid machine of the present invention, the radius 15 of the blade inlet 11 on the impeller rear surface shroud 5 side is set to r1s, and the radius of the blade outlet 12 on the impeller rear surface shroud 5 side, When the blade outlet rear surface shroud side radius 21 is r2s, the blade thickness 19 is changed from the impeller hub 3 side to the impeller rear surface shroud 5 side in the portion of the blade 4 where the blade radius r is smaller than r1s + (r2s−r1s) 2/3. It is gradually thinned. In this way, the blade inlet angle 16 of the centrifugal impeller 1 is further gradually reduced from the impeller hub 3 side toward the impeller rear surface shroud 5 side.

さらに、本発明の遠心流体機械のさらに他の実施の形態である遠心ポンプの遠心羽根車１は、図３（ａ）に示すように羽根車ハブ３のみを有し、羽根車後面シュラウド５を無くしたセミオープンの遠心羽根車１、又は図３（ｂ）に示すように、羽根車ハブ３を羽根を取付け得る範囲でできるだけ短くし、かつ、羽根車後面シュラウド５を無くしたフルオープンの遠心羽根車１である。このセミオープンの遠心羽根車１又はフルオープンの遠心羽根車１は固形物又は繊維物等のスラリーを汲みあげる遠心ポンプとするものであり、これらの遠心羽根車１は、羽根車ハブ３が長く、かつ、羽根車後面シュラウド５を有する遠心羽根車１に比べ固形物又は繊維物等のスラリーが詰まりにくい。   Furthermore, the centrifugal impeller 1 of the centrifugal pump which is still another embodiment of the centrifugal fluid machine of the present invention has only the impeller hub 3 as shown in FIG. As shown in FIG. 3 (b), the lost semi-open centrifugal impeller 1 or a full-open centrifugal where the impeller hub 3 is made as short as possible within the range in which the blades can be attached and the impeller rear surface shroud 5 is eliminated. The impeller 1. The semi-open centrifugal impeller 1 or the full-open centrifugal impeller 1 is a centrifugal pump for pumping slurry such as solids or fibers, and the centrifugal impeller 1 has a long impeller hub 3. And slurry, such as a solid substance or a fiber substance, is hard to be clogged compared with the centrifugal impeller 1 which has the impeller rear surface shroud 5.

遠心羽根車１の形状を上記のような形状とすることで、遠心羽根車１は量産用の金型から取り出しやすくなっている。このために遠心羽根車１の量産用の金型形状を簡易化することができ、この結果、遠心羽根車１の生産の効率化を図ることができる上に、羽根入口角１６を入口流れ角１７に合わせることができて遠心羽根車１の高効率化の実現を図ることができる。   By making the shape of the centrifugal impeller 1 as described above, the centrifugal impeller 1 can be easily taken out from a mass production mold. For this reason, the shape of the mold for mass production of the centrifugal impeller 1 can be simplified. As a result, the production efficiency of the centrifugal impeller 1 can be improved, and the blade inlet angle 16 is changed to the inlet flow angle. 17 and the high efficiency of the centrifugal impeller 1 can be realized.

遠心ポンプとしての遠心羽根車１の１種は、本発明の遠心羽根車１であり、羽根４の羽根圧力面６は二次元曲面形状からなり、かつ、羽根４の羽根負圧面７は三次元曲面形状からなるものである。一方、他の１種は従来の遠心羽根車１で、その羽根４は羽根圧力面６および羽根負圧面７が共に三次元曲面形状からなる羽根形状である。これらの２種の遠心羽根車１の羽根形状は異なっているが、その他の条件はすべて同じである。図２は本発明の遠心羽根車１の構造の断面図を示し、図５は、従来の三次元遠心羽根車１の構造の断面図を示している。   One type of centrifugal impeller 1 as a centrifugal pump is the centrifugal impeller 1 of the present invention, the blade pressure surface 6 of the blade 4 has a two-dimensional curved surface shape, and the blade negative pressure surface 7 of the blade 4 has a three-dimensional shape. It consists of a curved shape. On the other hand, the other type is a conventional centrifugal impeller 1 and its blade 4 has a blade shape in which the blade pressure surface 6 and the blade negative pressure surface 7 are both three-dimensional curved surfaces. Although these two types of centrifugal impellers 1 have different blade shapes, all other conditions are the same. FIG. 2 shows a sectional view of the structure of the centrifugal impeller 1 of the present invention, and FIG. 5 shows a sectional view of the structure of the conventional three-dimensional centrifugal impeller 1.

この本発明の実施例における遠心羽根車１の主要諸元を示すと、以下の通りである。
遠心羽根車１の外径はφ１２７．０ｍｍ、羽根出口１２における羽根角度は２５.００°、羽根出口１２における羽根高さ１８は１１．０ｍｍ、羽根出口１２における羽根厚み１９は５．０ｍｍ、羽根入口１１のハブ側の羽根角度は３３．３４°、羽根入口１１の中間部の羽根角度は２６．６１°、羽根入口１１の後面シュラウド側の羽根角度は２１．００°、羽根入口ハブ側半径１３は２３．０ｍｍ、羽根入口中間部半径１４は２７．７ｍｍ、羽根入口後面シュラウド側半径１５は３２．５ｍｍ、羽根枚数は５枚である。 The main specifications of the centrifugal impeller 1 in the embodiment of the present invention are as follows.
The outer diameter of the centrifugal impeller 1 is φ127.0 mm, the blade angle at the blade outlet 12 is 25.00 °, the blade height 18 at the blade outlet 12 is 11.0 mm, the blade thickness 19 at the blade outlet 12 is 5.0 mm, the blade The blade angle of the hub side of the inlet 11 is 33.34 °, the blade angle of the middle portion of the blade inlet 11 is 26.61 °, the blade angle of the rear shroud side of the blade inlet 11 is 21.00 °, the blade inlet hub side radius 13 is 23.0 mm, blade inlet middle radius 14 is 27.7 mm, blade inlet rear surface shroud side radius 15 is 32.5 mm, and the number of blades is five.

図７は本発明の遠心羽根車１を装備した遠心ポンプと、従来の遠心羽根車１を装備した遠心ポンプとの実測性能を比較して示すグラフで、揚水量Ｑ［Ｌ／ｍｉｎ］に対する全揚程Ｈ［ｍ］と、揚水量Ｑ［Ｌ／ｍｉｎ］に対する入力［Ｗ］の関係を示す。図８は本発明の遠心羽根車１を装備した遠心ポンプと、従来の遠心羽根車１を装備した遠心ポンプとの実測性能を比較して示すグラフで、揚水量Ｑ［Ｌ／ｍｉｎ］に対するポンプ効率［％］の関係を示す。本発明の遠心羽根車１をもつ遠心ポンプの全効率は、従来の三次元遠心羽根車をもつ遠心ポンプの全効率とほぼ同じ程度に達し、本発明形状の遠心羽根車１を採用することによって、遠心羽根車１の高効率化が実現されることがわかる。本発明の遠心羽根車１は上記したように、量産用の金型から取り出しやすい形状になっているため、本発明の遠心羽根車１の量産用の金型形状も簡易化でき、この結果、本発明の遠心羽根車１を量産する生産効率化を図ることができた。   FIG. 7 is a graph showing a comparison of measured performances between a centrifugal pump equipped with the centrifugal impeller 1 of the present invention and a centrifugal pump equipped with a conventional centrifugal impeller 1, and shows the total pumping amount Q [L / min]. The relationship between the head H [m] and the input [W] with respect to the pumping amount Q [L / min] is shown. FIG. 8 is a graph showing a comparison of measured performances between a centrifugal pump equipped with the centrifugal impeller 1 of the present invention and a centrifugal pump equipped with a conventional centrifugal impeller 1, and is a pump with respect to the pumping amount Q [L / min]. The relationship of efficiency [%] is shown. The total efficiency of the centrifugal pump having the centrifugal impeller 1 of the present invention reaches substantially the same as the total efficiency of the centrifugal pump having the conventional three-dimensional centrifugal impeller, and by adopting the centrifugal impeller 1 of the present invention shape. It can be seen that high efficiency of the centrifugal impeller 1 is realized. As described above, since the centrifugal impeller 1 of the present invention has a shape that can be easily taken out from the mold for mass production, the shape of the mold for mass production of the centrifugal impeller 1 of the present invention can be simplified. The production efficiency for mass production of the centrifugal impeller 1 of the present invention could be improved.

図９は本発明の遠心羽根車１を装備した遠心ポンプの実測騒音と従来の遠心羽根車１を装備した遠心ポンプの実測騒音を比較して示すグラフで、実測騒音は流量［Ｌ／ｍｉｎ］と騒音値［ｄＢ］で示す。本発明の遠心羽根車１をもつ遠心ポンプの騒音は、従来の三次元の遠心羽根車１をもつ遠心ポンプの騒音と比べ遥かに静音となっていることがわかる。   FIG. 9 is a graph showing a comparison between the measured noise of the centrifugal pump equipped with the centrifugal impeller 1 of the present invention and the measured noise of the centrifugal pump equipped with the conventional centrifugal impeller 1, and the measured noise is the flow rate [L / min]. And the noise value [dB]. It can be seen that the noise of the centrifugal pump having the centrifugal impeller 1 of the present invention is much quieter than that of the centrifugal pump having the conventional three-dimensional centrifugal impeller 1.

（ａ）は遠心羽根車を有する遠心ポンプを一部断面で示す側面図で、（ｂ）は遠心ポンプを断面で示す正面図である。(A) is a side view which shows the centrifugal pump which has a centrifugal impeller in a partial cross section, (b) is a front view which shows a centrifugal pump in a cross section. 本発明の遠心羽根車の構造を示し、（ａ）は羽根車の側面形状を示し、（ｂ）は羽根車の正面形状を示す模式図ある。The structure of the centrifugal impeller of this invention is shown, (a) shows the side shape of an impeller, (b) is a schematic diagram which shows the front shape of an impeller. 他の形態の遠心羽根車の一部断面図を示し、（ａ）はセミオープン羽根車を有する遠心ポンプの一部断面図を示し、（ｂ）はフルオープン羽根車を有する遠心ポンプの一部断面図を示す模式図である。The partial cross section figure of the centrifugal impeller of another form is shown, (a) shows the partial cross section figure of the centrifugal pump which has a semi-open impeller, (b) is a part of centrifugal pump which has a full open impeller It is a schematic diagram which shows sectional drawing. 羽根入口の速度三角形を説明する図である。It is a figure explaining the speed triangle of a blade inlet. 従来の三次元形状の遠心羽根車の構造を示し、（ａ）は羽根車の側面形状を示し、（ｂ）は羽根車の正面形状を示す模式図ある。The structure of the conventional centrifugal impeller of a three-dimensional shape is shown, (a) shows the side shape of an impeller, (b) is a schematic diagram which shows the front shape of an impeller. 従来の二次元形状の遠心羽根車の構造を示し、（ａ）は羽根車の側面形状を示し、（ｂ）は羽根車の正面形状を示す模式図ある。The structure of the conventional centrifugal impeller of the two-dimensional shape is shown, (a) shows the side shape of an impeller, (b) is a schematic diagram which shows the front shape of an impeller. 本発明の遠心羽根車を持つ遠心ポンプと従来の三次元形状の羽根車を持つ遠心ポンプの性能を比較するグラフで、揚水量Ｑに対する全揚程Ｈとポンプの入力の関係を示すグラフである。It is a graph which compares the performance of the centrifugal pump with the centrifugal impeller of this invention and the conventional centrifugal pump with a three-dimensional shape impeller, and is a graph which shows the relationship between the total head H with respect to the pumping amount Q, and the input of a pump. 本発明の遠心羽根車を持つ遠心ポンプと従来の三次元形状の羽根車を持つ遠心ポンプの性能を比較するグラフで、揚水量Ｑに対するポンプ効率の関係を示すグラフである。It is a graph which compares the performance of the centrifugal pump with the centrifugal impeller of this invention, and the centrifugal pump with the conventional three-dimensional shape impeller, and is a graph which shows the relationship of the pump efficiency with respect to the pumping amount Q. 本発明の遠心羽根車を持つ遠心ポンプと従来の三次元形状の羽根車を持つ遠心ポンプの騒音を比較するグラフで、流量に対する騒音値の関係を示すグラフである。It is a graph which compares the noise of the centrifugal pump with the centrifugal impeller of this invention, and the centrifugal pump with the conventional three-dimensional shape impeller, and is a graph which shows the relationship of the noise value with respect to flow volume.

符号の説明Explanation of symbols

１ 遠心羽根車
２ 渦巻室
３ 羽根車ハブ
４ 羽根
５ 羽根車後面シュラウド
６ 羽根圧力面
７ 羽根負圧面
８ ポンプ吸込口
９ ポンプ吐出口
１０ 羽根間流路
１１ 羽根入口
１２ 羽根出口
１３ 羽根入口ハブ側半径
１４ 羽根入口中間側半径
１６ 羽根入口角
１７ 入口流れ角
１８ 羽根高さ
１９ 羽根厚み
２０ ケーシング
２１ 羽根出口後面シュラウド側半径
２２ 流れの円周速度
２３ 流れの絶対速度
２４ 流れの相対速度 DESCRIPTION OF SYMBOLS 1 Centrifugal impeller 2 Swirl chamber 3 Impeller hub 4 Blade 5 Impeller rear surface shroud 6 Blade pressure surface 7 Blade negative pressure surface 8 Pump suction port 9 Pump discharge port 10 Flow path between blades 11 Blade inlet 12 Blade outlet 13 Blade inlet hub side Radius 14 Blade inlet intermediate radius 16 Blade inlet angle 17 Inlet flow angle 18 Blade height 19 Blade thickness 20 Casing 21 Blade outlet rear surface shroud side radius
22 Circumferential velocity of flow
23 Absolute velocity of flow
24 Relative velocity of flow

Claims (3)

遠心羽根車を有する遠心流体機械において、遠心羽根車の羽根圧力面を二次元曲面形状とし、羽根負圧面を三次元曲面形状とし、羽根車ハブ側の羽根厚みを羽根車後面シュラウド側の羽根厚みより厚くし、かつ、羽根厚みを羽根車ハブ側から羽根車後面シュラウド側に徐々に薄くしたことにより、遠心羽根車の羽根入口角を羽根車ハブ側から羽根車後面シュラウド側に向かって徐々に小さくしたことを特徴とする遠心羽根車。 In a centrifugal fluid machine having a centrifugal impeller, the blade pressure surface of the centrifugal impeller has a two-dimensional curved shape, the blade negative pressure surface has a three-dimensional curved shape, and the blade thickness on the impeller hub side is the blade thickness on the impeller rear surface shroud side. By increasing the blade thickness and gradually decreasing the blade thickness from the impeller hub side to the impeller rear surface shroud side, the blade inlet angle of the centrifugal impeller is gradually increased from the impeller hub side to the impeller rear surface shroud side. Centrifugal impeller characterized by being made small. 遠心羽根車は、羽根車後面シュラウド側の羽根入口半径をｒ１ｓとし、羽根車後面シュラウド側の羽根出口半径をｒ２ｓとするとき、羽根半径ｒがｒ１ｓ＋（ｒ２ｓ−ｒ１ｓ）２／３より小さい羽根部分において、羽根厚みを羽根車ハブ側から羽根車後面シュラウド側に徐々に薄くしたことにより、遠心羽根車の羽根入口角を羽根車ハブ側から羽根車後面シュラウド側に向かって徐々に小さくしたことを特徴とする請求項１に記載の遠心羽根車。 The centrifugal impeller has a blade portion whose blade radius r is smaller than r1s + (r2s−r1s) 2/3, where r1s is a blade inlet radius on the rear surface shroud side of the impeller and r2s is a blade outlet radius on the rear surface shroud side of the impeller. The blade inlet angle of the centrifugal impeller gradually decreases from the impeller hub side to the impeller rear shroud side by gradually reducing the blade thickness from the impeller hub side to the impeller rear shroud side. The centrifugal impeller according to claim 1, wherein 遠心羽根車は、羽根車ハブのみを有し羽根車後面シュラウドを無くしたセミオープン遠心羽根車又は羽根車ハブを短くしかつ羽根車後面シュラウドを無くしたフルオープン遠心羽根車からなることを特徴とする請求項１又は請求項２に記載の遠心羽根車。 The centrifugal impeller comprises a semi-open centrifugal impeller having only an impeller hub and having no impeller rear surface shroud, or a full open centrifugal impeller having a shorter impeller hub and no impeller rear shroud. The centrifugal impeller according to claim 1 or 2.
JP2004021783A 2004-01-29 2004-01-29 Centrifugal impeller Expired - Lifetime JP3949663B2 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2004021783A JP3949663B2 (en) 2004-01-29 2004-01-29 Centrifugal impeller
CNB2005100070081A CN100434723C (en) 2004-01-29 2005-01-31 Radial impeller

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2004021783A JP3949663B2 (en) 2004-01-29 2004-01-29 Centrifugal impeller

Publications (2)

Publication Number Publication Date
JP2004353655A JP2004353655A (en) 2004-12-16
JP3949663B2 true JP3949663B2 (en) 2007-07-25

Family

ID=34056300

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2004021783A Expired - Lifetime JP3949663B2 (en) 2004-01-29 2004-01-29 Centrifugal impeller

Country Status (2)

Country Link
JP (1) JP3949663B2 (en)
CN (1) CN100434723C (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11805765B1 (en) 2023-02-07 2023-11-07 Bradley Toschlog Centrifugal pump system

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008054587A1 (en) * 2008-12-12 2010-06-17 Basf Se Process for the cleavage of Michael adducts contained in a liquid F, which was formed during the production of acrylic acid or its esters
EP2614257A1 (en) * 2010-09-10 2013-07-17 Pratt & Whitney Rocketdyne Inc. Pumping element design
US10137264B2 (en) 2011-07-13 2018-11-27 Fisher & Paykel Healthcare Limited Respiratory assistance apparatus
US10286167B2 (en) 2011-07-13 2019-05-14 Fisher & Paykel Healthcare Limited Impeller and motor assembly
CA3108658A1 (en) * 2012-02-02 2014-01-09 Fisher & Paykel Healthcare Limited Respiratory assistance apparatus
AU2013365897A1 (en) 2012-12-18 2015-07-16 Fisher & Paykel Healthcare Limited Impeller and motor assembly
JP2014145269A (en) * 2013-01-28 2014-08-14 Asmo Co Ltd Vehicular pump device
CN103591046B (en) * 2013-11-12 2016-06-15 大连理工大学 A kind of high-power shield electric machine core main pump high-efficiency hydraulic model under multi-source constraint
CN104196731A (en) * 2014-08-20 2014-12-10 江苏超力电器有限公司 Brushless direct-current magnetic isolation type water pump
JP6758924B2 (en) * 2016-06-01 2020-09-23 株式会社クボタ Impeller
JP6758923B2 (en) * 2016-06-01 2020-09-23 株式会社クボタ Impeller
MX2017003271A (en) 2017-03-03 2017-08-31 Javier BUSTAMANTE SANDOVAL Francisco Mechanism for the propulsion of centrifugal pump blades to transport liquids and live fauna.
CN114288513A (en) 2017-04-23 2022-04-08 费雪派克医疗保健有限公司 Breathing assistance apparatus
CN108468654A (en) * 2018-04-09 2018-08-31 张家港市海工船舶机械制造有限公司 A kind of half-opened impeller and its manufacturing method
CN110909422B (en) * 2019-10-22 2021-06-04 浙江理工大学 Method for predicting and optimizing range of efficient working condition area of centrifugal pump impeller

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2661986B2 (en) * 1988-09-30 1997-10-08 松下冷機株式会社 Centrifugal blower impeller
JPH0589893U (en) * 1992-05-11 1993-12-07 株式会社川本製作所 Centrifugal pump
JP2871515B2 (en) * 1995-03-06 1999-03-17 松下冷機株式会社 Centrifugal blower

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11805765B1 (en) 2023-02-07 2023-11-07 Bradley Toschlog Centrifugal pump system

Also Published As

Publication number Publication date
CN100434723C (en) 2008-11-19
CN1648463A (en) 2005-08-03
JP2004353655A (en) 2004-12-16

Similar Documents

Publication Publication Date Title
JP3949663B2 (en) Centrifugal impeller
US9163642B2 (en) Impeller and rotary machine
JP4674206B2 (en) Improved pump impeller
WO2011043125A1 (en) Impeller of centrifugal compressor
JP5879103B2 (en) Centrifugal fluid machine
CN102365464B (en) impeller and rotary machine
KR101913147B1 (en) Centrifugal impeller having backward blades using dual gradient sectional shape type
JP2006002689A (en) Fan
WO2019172422A1 (en) Diffuser vane and centrifugal compressor
JP2015212551A (en) Centrifugal fluid machine
JP4209362B2 (en) Centrifugal compressor
JP4655603B2 (en) Centrifugal compressor
JP4174693B2 (en) Centrifugal compressor diffuser
US20160061213A1 (en) Pump Impeller
JP2016528438A (en) Diffuser for forward sweep tangential flow compressor
JP2010190221A (en) Blower
JP5207928B2 (en) Centrifugal pump
JP7146364B2 (en) centrifugal compressor
WO2011065039A1 (en) Centrifugal pump
KR100824149B1 (en) Centrifugal blower and air conditioner with centrifugal blower
JP4183634B2 (en) Centrifugal fluid machine
JP6138009B2 (en) Centrifugal turbomachine
KR102558158B1 (en) Centrifugal impeller with partially opened shroud
JP6758924B2 (en) Impeller
WO2011135663A1 (en) Centrifugal pump

Legal Events

Date Code Title Description
A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20070123

A521 Request for written amendment filed

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20070326

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20070417

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20070418

R150 Certificate of patent or registration of utility model

Ref document number: 3949663

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R150

Free format text: JAPANESE INTERMEDIATE CODE: R150

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20100427

Year of fee payment: 3

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20130427

Year of fee payment: 6

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20160427

Year of fee payment: 9

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

EXPY Cancellation because of completion of term