JPH04203395A - Turbo pump - Google Patents
Turbo pumpInfo
- Publication number
- JPH04203395A JPH04203395A JP32929390A JP32929390A JPH04203395A JP H04203395 A JPH04203395 A JP H04203395A JP 32929390 A JP32929390 A JP 32929390A JP 32929390 A JP32929390 A JP 32929390A JP H04203395 A JPH04203395 A JP H04203395A
- Authority
- JP
- Japan
- Prior art keywords
- flow
- vane
- blade
- hole
- pump
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 13
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 3
- 230000000149 penetrating effect Effects 0.000 claims 1
- 238000000034 method Methods 0.000 abstract description 2
- 238000002347 injection Methods 0.000 abstract 5
- 239000007924 injection Substances 0.000 abstract 5
- 230000001105 regulatory effect Effects 0.000 abstract 3
- 230000000694 effects Effects 0.000 description 5
- 230000015572 biosynthetic process Effects 0.000 description 3
- 238000000926 separation method Methods 0.000 description 3
- 230000000593 degrading effect Effects 0.000 description 2
- 241000282994 Cervidae Species 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 210000003746 feather Anatomy 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野]
本発明はポンプにおいてキャビテーション低減を図るた
めの、ポンプの羽根車形状に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a pump impeller shape for reducing cavitation in a pump.
〔従来の技術j
ポンプは大流量から小流量の広い流量範囲で運転される
。そこで、設計流量点から外れた大流量。[Prior Art J] Pumps are operated in a wide flow range from large flow rates to small flow rates. Therefore, the large flow rate deviated from the design flow point.
小流量の運転状態では羽根に流入する流れは羽根人「1
形状に沿わないで迎角がつき、流れは羽根面から剥離し
てキャビティ (空洞部)が生じる。In the operating state of small flow rate, the flow flowing into the impeller is ``1''.
The angle of attack increases without following the shape, and the flow separates from the blade surface, creating a cavity.
このため、羽根間の流路は狭められポンプの性能低下を
まねいたり、また、キャビティは下流に運ばれるにつれ
て消滅したり不安定な流れになり、羽根面を損傷させた
り、振動、騒音の原因となる。For this reason, the flow path between the blades is narrowed, leading to a decrease in pump performance, and the cavity disappears as it is carried downstream, resulting in unstable flow, which can damage the blade surface and cause vibration and noise. becomes.
このような悪影響をさけるため、例えば、従来の装置は
特願昭53−72152号明細−トに記載のように、羽
根jlLの前面あるいは背面のディスクとケーシングに
よって形成される間隙部と連続する連通孔を羽根01j
縁部に設けて、間隙部からの圧力水を羽根面から噴出さ
せて、羽根に迎角がついた場合の羽根人1」からの剥離
によるキャビティの発生を防止していた。In order to avoid such adverse effects, for example, conventional devices have a continuous communication with the gap formed by the disk and the casing on the front or back of the blade jlL, as described in Japanese Patent Application No. 72152/1983. Feather hole 01j
It was provided at the edge of the blade to eject pressure water from the gap from the blade surface to prevent cavities from forming due to separation from the blade when the blade is at an angle of attack.
この方法では、流bkの変化による迎角のつき方(圧力
面側あるいは負圧面側)に関係なく、常に圧力水を羽根
の両i/+iから噴出するようになっている。このため
、剥離が生じない面からの噴流はかえって流れを乱すこ
とになり、ポンプの性能低ドの原因となる。また、羽根
の内部に連通孔を設けることは製作コストも高くなる。In this method, pressurized water is always ejected from both i/+i of the blade, regardless of the angle of attack (pressure side or suction side) due to changes in flow bk. For this reason, the jet flow from the surface where separation does not occur will instead disturb the flow, causing a decrease in the performance of the pump. Further, providing a communication hole inside the blade increases manufacturing cost.
〔発明が解決しようとする課題]
本発明の目的は設計流量点を外れた大流量、小流歌詩の
いずれの場合にも、ポンプの性能を低下させることなく
傾角が大きくなって羽根入口から剥離して生じるキャビ
ティの発生を低減することにある。[Problems to be Solved by the Invention] The purpose of the present invention is to increase the angle of inclination without degrading the performance of the pump in both cases of large flow rate and small flow rate that are outside the design flow point. The purpose is to reduce the occurrence of cavities caused by peeling.
1−記1−1的を達成するために、本発明は羽根+1z
の羽根nf縁の上流に、羽根入口形状に沿った整流翼を
配置し、その整流翼には翼のif縁部と後縁部を貫通さ
せた噴流孔を設け、その噴流孔の入口は導水部とし、出
口形状は流路断面積が大きくなるテーパ状の拡大部を持
つようにしたものである。In order to achieve the objective 1-1, the present invention
A straightening blade that follows the blade inlet shape is arranged upstream of the blade nf edge, and the straightening blade is provided with a jet hole that penetrates the if edge and trailing edge of the blade. The outlet shape is such that it has a tapered enlarged part that increases the cross-sectional area of the flow path.
〔作11月
整流翼に設けた噴流孔は入口が導水部で出口が拡大部と
なっている。また、噴流孔の拡大部の流路断面形状は後
方に位置する羽根の圧力面、負圧面に沿うようなテーパ
状にしている。[Made in November] The jet holes installed in the rectifier blade have an inlet as a water guide part and an outlet as an enlarged part. Further, the cross-sectional shape of the passage in the enlarged part of the jet hole is tapered along the pressure surface and negative pressure surface of the blade located at the rear.
これによって、非設計流量点の大流量、小流11を時に
おいて異なる迎角をもつ流れが羽根に流入する場合、導
水部に流入し、テーパ状に広がった拡大部を流出する流
れは迎角の付き方によって後方の羽根人11の圧力場の
状態が変化する。そこで、その圧力場の圧力差の影響で
コアンダ効果が作用して、羽根の圧力面側に迎角がつく
場合は羽根の圧力面個人1−1に、羽根の負圧面側に迎
角がつく場合には羽根入[1の負圧面側に噴流となって
供給されるので、剥離によるキャビティの発生を防ぐこ
とができる。As a result, when a large flow rate at a non-design flow point and a flow having a different angle of attack at a small flow point 11 flow into the blade, the flow that flows into the water guide section and flows out through the tapered expanded section has an angle of attack of The state of the pressure field of the rear wing man 11 changes depending on how it is attached. Therefore, if the Coanda effect acts under the influence of the pressure difference in the pressure field and an angle of attack is created on the pressure side of the blade, an angle of attack is created on the pressure side of the blade (individual 1-1) and on the negative pressure side of the blade. In this case, since it is supplied in the form of a jet to the negative pressure side of the vane insert [1], it is possible to prevent the formation of cavities due to peeling.
また、導水部の人11の流路断面形状は流量の変化によ
る流れの方向の変化を考慮に入れてテーパ状にする流れ
をスムースに導びくことができ、噴流孔出自の拡大部か
らの噴流のエネルギが大きくなり、より−層キャビティ
の発生を防止する効果がある。In addition, the flow path cross-sectional shape of the water guide section 11 can smoothly guide a tapered flow by taking into account changes in the flow direction due to changes in flow rate, and the jet flow from the enlarged part of the jet hole originates. The energy becomes larger, which is more effective in preventing the formation of layer cavities.
以下、本発明の一実施例を第1図および第2図により説
明する。An embodiment of the present invention will be described below with reference to FIGS. 1 and 2.
羽根+l(lの羽根1);j縁2Q)]−流には、シュ
ラウド側板3とボス壁4に固定された整流翼5が配置さ
れ、その整流翼には整流翼の前縁部6と後縁部7を(′
1通ずる1(“を流孔8を設け、その噴流孔の人1−1
は流れの方向の変化を考慮に入れた導水部とし、噴流孔
の11冒1形状は噴流の流出方向が羽根の圧力面、負圧
面に沿うようなテーパ状の拡大部としている。。Vane +l (blade 1 of l; j edge 2Q)] - A straightening vane 5 fixed to the shroud side plate 3 and boss wall 4 is arranged in the flow, and the straightening vane has a leading edge 6 of the straightening vane and The trailing edge 7 is ('
1 to 1
is a water guide part that takes into account changes in the flow direction, and the shape of the jet hole is a tapered enlarged part so that the outflow direction of the jet flow follows the pressure surface and negative pressure surface of the blade. .
これにより、非設計流量点1点で迎角を持って流れが羽
根に流入する場合、噴流孔の導水部9を通って噴流孔の
拡大部10を流出する流れは迎角のつき方によって、後
方の羽根六[lの圧力場の変化の影響を受けてコアンダ
効果が作用し、羽根の圧力1(、H+ +側に迎角がつ
く流れの場合は羽根め圧力面側人11に、羽根の負圧面
12側に迎角がつく流れの場合は羽根の負圧面何人IJ
に117’χ流となって供給されるので、迎角がつく非
設計流量点での流れも、羽根人j1からA離しやすい羽
根面側だけに噴流が供給されるので、ポンプの性能を低
ドさせることなくキャビティの発生を1坊止できる。As a result, when a flow flows into the blade with an angle of attack at one non-design flow point, the flow passing through the water guide part 9 of the jet hole and flowing out of the enlarged part 10 of the jet hole depends on the angle of attack. Under the influence of the change in the pressure field of the rear blade 6 [l, the Coanda effect acts, and in the case of a flow where the angle of attack is on the + side, the blade pressure side 11 is In the case of a flow where the angle of attack is on the suction side 12 of the blade, how many people on the suction side of the blade IJ
Since the flow is supplied as a 117'χ flow, even at a non-design flow point where the angle of attack occurs, the jet flow is supplied only to the blade surface side where it is easy to separate A from the blade man j1, reducing the performance of the pump. The occurrence of cavities can be prevented by one step without causing any damage.
第3図はその他の実施例を示す5.第2図の実施例の場
合と異なる所は、整流翼5に設けた導水部9の形状をテ
ーパ状の縮流形状にして、運転流量の変化によって迎角
の変化する流れが導水部にス=4−
ムースに流入できるようにした場合である。第2図の場
合より、迎角がつく流れをスムーズに導水部へ導びくこ
とがでるので、剥離しゃすい羽根人[1へ供給する噴流
のエネルギは大きくなり、キャビティージョンの発生を
紡ぐ効果は大きくなる。FIG. 3 shows another embodiment 5. The difference from the embodiment shown in FIG. 2 is that the shape of the water guide section 9 provided on the straightening blade 5 is made into a tapered contracted flow shape, so that the flow whose angle of attack changes depending on the change in the operating flow rate is directed to the water guide section. =4- This is the case where it is possible to flow into the moose. Compared to the case shown in Fig. 2, the flow with an angle of attack can be guided smoothly to the water guide section, so the energy of the jet supplied to the separation impeller [1] increases, which has the effect of preventing the occurrence of cavity johns. becomes larger.
本発明によれば、羽根前縁の1−流に設けた噴流孔を持
つ整流翼により、ポンプの性能を低ドさせることなくキ
ャビティの発生を防ぐことができるので、羽根の損傷お
よびポンプの振動、騒音を低減することができる。According to the present invention, the rectifier vane having the jet hole provided in the first stream at the leading edge of the vane can prevent the formation of cavities without degrading the performance of the pump, thereby preventing damage to the vanes and vibration of the pump. , noise can be reduced.
第1図は本発明の−・実施例の縦断面図、第2図。 第:3図は第1図のA−A親展IJIJ図である。 FIG. 1 is a vertical sectional view of an embodiment of the present invention, and FIG. 2 is a longitudinal sectional view of an embodiment of the present invention. Figure 3 is an A-A confidential IJIJ diagram of Figure 1.
Claims (1)
とボス壁に固定した整流翼を配置し、前記整流翼には翼
の前縁部と後縁部を貫通させた噴流孔を設け、前記噴流
孔の入口は導水部を出口は流路断面積が大きくなる拡大
部をそれぞれ設けたことを特徴とするターボ形ポンプ。1. A straightening vane fixed to the shroud side plate and the boss wall is arranged upstream of the leading edge of the blade of the impeller of the pump, and the straightening vane is provided with a jet hole penetrating the leading edge and the trailing edge of the blade, A turbo pump characterized in that the inlet of the jet hole is provided with a water guiding part, and the outlet thereof is provided with an enlarged part in which the cross-sectional area of the flow passage becomes large.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP32929390A JPH04203395A (en) | 1990-11-30 | 1990-11-30 | Turbo pump |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP32929390A JPH04203395A (en) | 1990-11-30 | 1990-11-30 | Turbo pump |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH04203395A true JPH04203395A (en) | 1992-07-23 |
Family
ID=18219844
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP32929390A Pending JPH04203395A (en) | 1990-11-30 | 1990-11-30 | Turbo pump |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH04203395A (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6007300A (en) * | 1996-05-17 | 1999-12-28 | Calsonic Corporation | Centrifugal multiblade fan |
-
1990
- 1990-11-30 JP JP32929390A patent/JPH04203395A/en active Pending
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6007300A (en) * | 1996-05-17 | 1999-12-28 | Calsonic Corporation | Centrifugal multiblade fan |
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