JPH0270992A - High speed turbopump - Google Patents
High speed turbopumpInfo
- Publication number
- JPH0270992A JPH0270992A JP22053388A JP22053388A JPH0270992A JP H0270992 A JPH0270992 A JP H0270992A JP 22053388 A JP22053388 A JP 22053388A JP 22053388 A JP22053388 A JP 22053388A JP H0270992 A JPH0270992 A JP H0270992A
- Authority
- JP
- Japan
- Prior art keywords
- impeller
- suction guide
- suction
- guide device
- diameter
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000007423 decrease Effects 0.000 claims description 5
- 238000011144 upstream manufacturing Methods 0.000 claims description 5
- 238000005192 partition Methods 0.000 claims description 2
- 239000012530 fluid Substances 0.000 abstract description 5
- 238000000034 method Methods 0.000 abstract description 2
- 230000002093 peripheral effect Effects 0.000 abstract description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 11
- 230000000694 effects Effects 0.000 description 3
- 238000002474 experimental method Methods 0.000 description 2
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000000052 comparative effect Effects 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000007704 transition Effects 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、周方向に細かく分けられた複数の吸込流路を
区画する吸込案内羽根を有する吸込案内装置を羽根車の
上流側に備え、前記吸込流路の断面積が羽根車の羽根入
口縁に向かって羽根車の回転方向に次第に縮小するよう
に形成された吸込案内装置を有する形式の高速ターボポ
ンプに関する。DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention provides a suction guide device provided on the upstream side of an impeller, which has suction guide vanes that partition a plurality of suction channels finely divided in the circumferential direction. The present invention relates to a high-speed turbo pump having a suction guide device formed such that the cross-sectional area of the suction passage gradually decreases in the direction of rotation of the impeller toward the blade inlet edge of the impeller.
ターボ形ポンプを高速化しかつ小型化しようとするとき
、小容量高揚程のポンプは容易に製作することができる
。というのは、発生揚程は羽根車外周速度の二乗(従っ
て回転数の二乗)に比例しかつ流量が回転数に比例する
ので、羽根外径を小さくして高速化できるからである。When trying to speed up and downsize turbo pumps, small capacity, high head pumps can be easily manufactured. This is because the head generated is proportional to the square of the impeller outer peripheral speed (therefore, the square of the rotational speed) and the flow rate is proportional to the rotational speed, so it is possible to increase the speed by reducing the outer diameter of the impeller.
羽根車の上流に吸込案内装置を備えた形式のこのような
小容量高揚程の高速ポンプの一例として、本出願人の特
許出願63−34070のターボポンプがある。An example of such a small-capacity, high-head, high-speed pump with a suction guide device upstream of the impeller is the turbo pump of patent application 63-34070 of the present applicant.
この出願で用いられる吸込案内装置を比較的内外径比の
大きい羽根車でかつ羽根長さの短い羽根車を有する形式
の高速ターボポンプに適用した例を第8図に示す。ここ
で言う羽根内外径比は羽根車外径d2と内径d1の比a
l/azを意味する。ポンプケーシング41内に突出す
る回転軸42の端部に内外径比が大きくかつ羽根長さの
比較的短い羽根車43が固定され、羽根車43の羽根4
4を囲むようにポリュートケーシング部分45が配置さ
れている。ポリュートケーシング部分45の内側に、羽
根車43の羽根44の上流に羽根44に隣接して前述し
た吸込案内装置46が取外し可能に装着され、この吸込
案内装置の上流にさらに吸込ケーシング47が取りつけ
られている。吸込案内装置46の入口側には、複数個の
入口48が配置されており、第9図から分かるように、
これらの入口から延びる軸方向のもしくは軸方向に対し
羽根車回転方向に傾けた各流入孔49が吸込案内装置の
出口側で、羽根車43の羽根44に向かう周方向流路に
なめらかな曲線を描いて移行し、その各周方向流路は、
その断面積が羽根車43の羽根入口縁44aに向かって
羽根車の回転方向に次第に縮小するように形成されてい
る。吸込案内装置の吸込案内口径dは、羽根車の羽根入
口径d、にほぼ等しく、かつ吸込ケーシングのポンプ吸
込口径りは吸込案内口径dに等しい。FIG. 8 shows an example in which the suction guide device used in this application is applied to a high-speed turbo pump having an impeller with a relatively large inner/outer diameter ratio and a shorter blade length. The blade inner and outer diameter ratio referred to here is the ratio a of the impeller outer diameter d2 and inner diameter d1.
means l/az. An impeller 43 having a large inner/outer diameter ratio and a relatively short blade length is fixed to the end of the rotating shaft 42 protruding into the pump casing 41.
A polyte casing portion 45 is arranged so as to surround 4. Inside the porute casing part 45, upstream of and adjacent to the blades 44 of the impeller 43, the aforementioned suction guide device 46 is removably mounted, and further upstream of this suction guide device, a suction casing 47 is mounted. It is being A plurality of inlets 48 are arranged on the inlet side of the suction guide device 46, and as can be seen from FIG.
Each inlet hole 49 extending from these inlets in the axial direction or inclined in the direction of rotation of the impeller with respect to the axial direction forms a smooth curve in the circumferential flow path toward the blades 44 of the impeller 43 on the outlet side of the suction guide device. Draw and transition, and each circumferential flow path is
The cross-sectional area thereof is formed so as to gradually decrease in the direction of rotation of the impeller toward the blade inlet edge 44a of the impeller 43. The suction guide diameter d of the suction guide device is approximately equal to the blade inlet diameter d of the impeller, and the pump suction diameter of the suction casing is equal to the suction guide diameter d.
このような設計により、羽根車の羽根入口での急激な流
れの方向変化を起こさずに羽根車の羽根の中へ流体を流
入させることができ、羽根車の羽根入口における損失が
大幅に低減され、ポンプの高速化が可能となる。この吸
込案内装置を独特の構成の羽根車と組み合わせることに
よりポンプの揚程特性曲線の右下がりの度合いの大きな
高揚程小容量のターボポンプを比較的容易に得ることが
できる。Such a design allows fluid to flow into the impeller blades without abrupt flow direction changes at the impeller blade inlet, significantly reducing losses at the impeller blade inlet. , it becomes possible to increase the speed of the pump. By combining this suction guide device with an impeller having a unique configuration, it is possible to relatively easily obtain a high-head, small-capacity turbo pump with a large downward slope of the pump head characteristic curve.
しかしながら、現在、従来の設計法で製作されている比
較的大きな容量の汎用ポンプ並みの特性を例えば100
00 r、ρ3m程度の高速で実現しようとすると、当
然の結果として速度を速くすればするほど羽根車の外径
が非常に小さくなり、羽根車の内外径比を小さく設計し
たとしても、これに伴って羽根入口径も小さくなる。こ
の羽根入口径に合わせたポンプの吸込口径にすると、羽
根出口幅を広(取り、流量の大きい設計としたとしても
、ポンプ流量はこの吸込口径によって決められて小さく
なってしまう。その結果、前述したような小流量高揚程
ポンプしか設計できないことになり、比較的容量の大き
い汎用ポンプの高速化が計れない。However, at present, for example, 100 pumps have the same characteristics as relatively large capacity general-purpose pumps manufactured using conventional design methods.
If we try to achieve a high speed of about 00 r, ρ3m, the natural result is that the faster the speed is, the smaller the outer diameter of the impeller becomes. Accordingly, the blade inlet diameter also becomes smaller. If the suction port diameter of the pump is set to match this impeller inlet diameter, even if the impeller outlet width is widened and the flow rate is designed to be large, the pump flow rate will be determined by this suction port diameter and will be small. This means that only small-flow, high-head pumps like the one above can be designed, making it impossible to increase the speed of general-purpose pumps with relatively large capacities.
従って、本発明の目的は、比較的容量の大きい汎用ポン
プ並みの特性を高速で実現することができるターボポン
プを提供することである。Therefore, an object of the present invention is to provide a turbo pump that can achieve characteristics similar to those of a general-purpose pump with a relatively large capacity at high speed.
上記の目的を達成するために、本発明により、吸込案内
装置の吸込案内口径(d)を羽根車の羽根入口径より大
きくし、その吸込案内口径を羽根車の羽根入口径から羽
根外径までの任意の値とすることにより前記の不具合が
解決される。In order to achieve the above object, the present invention makes the suction guide diameter (d) of the suction guide device larger than the blade inlet diameter of the impeller, and extends the suction guide diameter from the blade inlet diameter of the impeller to the blade outer diameter. The above problem can be solved by setting the value to an arbitrary value.
以下、本発明を実施例について図面により説明する。 DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be explained below with reference to embodiments.
第1図に本発明による高速ターボポンプ140の第一実
施例の縦断面を示す。第8図および第9図と同様な部品
にはその参照数字に100をプラスしである。FIG. 1 shows a longitudinal section of a first embodiment of a high-speed turbo pump 140 according to the present invention. Parts similar to FIGS. 8 and 9 have their reference numerals plus 100.
これまでの吸込案内装置の吸込案内口径は羽根車の羽根
入口径d1に等しいが、本発明により、後述する理由か
ら吸込案内装置146の吸込案内口径dを羽根車143
の羽根144の外形dz近くまで大きくしである。それ
に応じてポンプ吸込口径りも図示のように大きくできる
。The suction guide aperture of the conventional suction guide device is equal to the blade inlet diameter d1 of the impeller, but according to the present invention, the suction guide aperture d of the suction guide device 146 is set to
The outer diameter of the blade 144 is increased to nearly dz. Accordingly, the diameter of the pump suction port can be increased as shown.
吸込案内装置146を下流側端面より見た第2図から分
かるように、吸込案内装置の拡大された各吸込口148
より流入した流体は、なめらかなカーブに沿って吸込案
内装置の出口側の周方向流路に入るが、大部分が羽根車
143の回転方向に次第に横断面積の縮小する流路に沿
って羽根車143の羽根入口縁144aに向かって流れ
、一部が羽根144の縦縁144bの側から羽根に流入
する。As can be seen from FIG. 2, which shows the suction guide device 146 from the downstream end, each of the enlarged suction ports 148 of the suction guide device
The more inflowing fluid enters the circumferential flow path on the outlet side of the suction guide device along a smooth curve, but most of the fluid flows through the impeller 143 along a flow path whose cross-sectional area gradually decreases in the rotation direction of the impeller 143. It flows toward the blade inlet edge 144a of the blade 143, and a portion flows into the blade from the longitudinal edge 144b side of the blade 144.
吸込案内装置146の吸込案内口径を羽根車の羽根外径
近(まで拡げた本発明による構成は、次に示す実験によ
り立証される。この実験は、内燃機関の冷却装置に用い
られる内外径比が太き(て羽根車の羽根長さが比較的短
いウオータポンプであって、同一の羽根でかつ同一の吐
出ケーシングで入口形状を種々変化させた四種類のウォ
ータポンプを用いて行われた。The configuration according to the present invention in which the suction guide aperture of the suction guide device 146 is expanded to near the outside diameter of the blades of the impeller is proven by the following experiment. The tests were conducted using four types of water pumps with relatively short impeller blades, each with the same blades and the same discharge casing, but with various inlet shapes.
第3図は、通常のポンプ設計の概念により構成された従
来のウォータポンプN001で、回転軸31に固定され
た羽根車32の羽根入口径に対応する内径を有するフロ
ントリング33が取りつけられていて、吸込案内装置が
設けられていない。34aはポンプ吸込口、35は吐出
ケーシングである。FIG. 3 shows a conventional water pump N001 constructed according to the concept of normal pump design, in which a front ring 33 having an inner diameter corresponding to the diameter of the impeller inlet of an impeller 32 fixed to a rotating shaft 31 is attached. , no suction guide device is provided. 34a is a pump suction port, and 35 is a discharge casing.
第4図は、第3図のフロントリング33がなく、吸込口
径34bが同一の羽根車32の外径に対応しており、吸
込案内装置が設けられていないウォータポンプでN09
2である。FIG. 4 shows a water pump N09 in which the front ring 33 of FIG. 3 is absent, the suction port diameter 34b corresponds to the outer diameter of the same impeller 32, and the suction guide device is not provided.
It is 2.
第5図は、複数の流路の断面積が羽根車32の羽根入口
縁32aに向かって半径方向に次第に縮小するように形
成された吸込案内装置36が設けられたウォーターポン
プN003で、吸込案内口径dが羽根車32の羽根入口
径に対応している。FIG. 5 shows a water pump N003 equipped with a suction guide device 36 in which the cross-sectional area of a plurality of flow paths gradually decreases in the radial direction toward the blade inlet edge 32a of the impeller 32. The aperture d corresponds to the blade inlet diameter of the impeller 32.
第6図は、第5図の吸込案内装置36の吸込案内口径d
を羽根車の入口径d、より大きくかつ羽根車の羽根外径
d2より小さく構成された本発明による吸込案内装置を
備えたウォータポンプNo、4である。FIG. 6 shows the suction guide diameter d of the suction guide device 36 in FIG.
Water pump No. 4 is equipped with a suction guide device according to the present invention, which is larger than the impeller inlet diameter d and smaller than the impeller blade outer diameter d2.
第7図にこれらの四種類のウォータポンプの実験結果を
グラフで示す。ここで、羽根車の回転数は7800r、
p、mである。揚程特性曲線を見ると、フロントリン
グを除いた羽根車外径までの吸込口径を有するNo、2
のみが、揚程が低下しているが、他のN o −1−、
N o 、4はほぼ同じ揚程が得られていることが分か
る。さらに、軸動力曲線を見ると、吸込案内装置を取り
つけたウオークポンプNo、3、No、4の所要軸動力
が流量の高い使用範囲で吸込案内装置を有しないウォー
タポンプNo、1より低くなっており、能率が良いこと
が分かる。また、吸込案内装置の吸込案内口径を羽根車
の羽根入口径から羽根外径近くにしても所要軸動力が変
わらないことが分かる。これらの結果から分かるように
、本発明のウォータポンプNo、4は、従来のウォータ
ポンプNo、1よりいっそう少ない動力で従来と変わら
ない揚程特性をもって輸送することができる。FIG. 7 graphically shows the experimental results of these four types of water pumps. Here, the rotation speed of the impeller is 7800r,
p, m. Looking at the head characteristic curve, No. 2 has a suction diameter up to the outer diameter of the impeller excluding the front ring.
The head of only N o -1- is reduced, but the other N o -1-,
It can be seen that almost the same head is obtained for No. 4. Furthermore, looking at the shaft power curve, the required shaft power of walk pumps No. 3, No. 4, which are equipped with a suction guide device, is lower than that of water pump No. 1, which does not have a suction guide device, in the high flow range of use. It can be seen that the efficiency is good. Furthermore, it can be seen that the required shaft power does not change even if the suction guide diameter of the suction guide device is changed from the impeller blade inlet diameter to close to the blade outer diameter. As can be seen from these results, the water pump No. 4 of the present invention can transport with less power than the conventional water pump No. 1 and with the same head characteristics as the conventional water pump.
また、羽根車の羽根長さおよびケーシングと羽根の間の
隙間の影響を実験により調べた結果、成る羽根長さ以下
の羽根車で、成る回転数以上になると、揚程特性曲線に
ほとんど影響がないことが分かった。In addition, as a result of experimenting to investigate the effects of the impeller blade length and the gap between the casing and the blades, it was found that with an impeller with a blade length less than or equal to 1, there is almost no effect on the head characteristic curve when the rotation speed is greater than or equal to 1. That's what I found out.
本発明では、吸込案内装置の吸込案内口径を羽根車の入
口径より大きくし、その吸込案内口径を羽根車の羽根入
口径から羽根外径までの任意の値にしたにもかかわらず
、前述した実験結果から立証されるように、揚程特性が
従来と変わりなく、しかも動力が少なくてすむので、比
較的大きい流量範囲をもつ高速ポンプの設計が容易にな
り、汎用化が可能になる。In the present invention, the suction guide aperture of the suction guide device is made larger than the inlet diameter of the impeller, and the suction guide aperture is set to an arbitrary value from the impeller blade inlet diameter to the blade outer diameter. As evidenced by the experimental results, the pump head characteristics remain the same as before, and less power is required, making it easier to design a high-speed pump with a relatively large flow range and making it more versatile.
第1図は本発明による高速ターボポンプの一実施例の縦
断面図、第2図は第1図のターボポンプの吸込案内装置
を線n−ttに沿って見た端面図、第3図〜第6図は本
発明のターボポンプの比較実験をするために用いられた
内燃機関の冷却用の四種類のウォータポンプの概略図、
第7図はその実験結果を示すグラフ、第8図は吸込案内
装置を用いた従来の小容量高揚程のターボポンプの縦断
面図、第9図は第8図の吸込案内装置の端面図である。
143.243・−・羽根車、144a、244a・・
・羽根入口縁、144,244・・・羽根、146,2
46・・・吸込案内装置、149.249・・・吸込案
内羽根、d・・・吸込案内口径、d、・・・羽根車の羽
根入口径、d2 ・・・羽根車の羽根外径FIG. 1 is a longitudinal sectional view of an embodiment of a high-speed turbo pump according to the present invention, FIG. 2 is an end view of the suction guide device of the turbo pump of FIG. 1 taken along line n-tt, and FIGS. FIG. 6 is a schematic diagram of four types of water pumps for cooling internal combustion engines used for comparative experiments of the turbo pump of the present invention;
Fig. 7 is a graph showing the experimental results, Fig. 8 is a vertical cross-sectional view of a conventional small-capacity, high-head turbo pump using a suction guide device, and Fig. 9 is an end view of the suction guide device shown in Fig. 8. be. 143.243--Impeller, 144a, 244a...
・Blade inlet edge, 144,244...Blade, 146,2
46... Suction guide device, 149.249... Suction guide vane, d... Suction guide diameter, d,... Impeller blade inlet diameter, d2... Impeller blade outer diameter
Claims (1)
する吸込案内羽根を有する吸込案内装置を羽根車の上流
側に備え、前記吸込流路の断面積が羽根車の羽根入口縁
に向かって羽根車の回転方向に次第に縮小するように形
成された吸込案内装置の吸込案内口径(d)を羽根車の
羽根入口径より大きくし、その吸込案内口径を羽根車の
羽根入口径から羽根外径までの任意の値としたことを特
徴とする高速ターボポンプ。(1) A suction guide device having suction guide vanes that partition a plurality of suction channels finely divided in the circumferential direction is provided on the upstream side of the impeller, and the cross-sectional area of the suction channel is located at the blade inlet edge of the impeller. The suction guide diameter (d) of the suction guide device, which is formed to gradually decrease in the rotational direction of the impeller, is made larger than the blade inlet diameter of the impeller. A high-speed turbo pump characterized by having an arbitrary value up to the outer diameter.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP22053388A JPH0749798B2 (en) | 1988-09-05 | 1988-09-05 | High speed turbo pump |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP22053388A JPH0749798B2 (en) | 1988-09-05 | 1988-09-05 | High speed turbo pump |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH0270992A true JPH0270992A (en) | 1990-03-09 |
JPH0749798B2 JPH0749798B2 (en) | 1995-05-31 |
Family
ID=16752487
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP22053388A Expired - Lifetime JPH0749798B2 (en) | 1988-09-05 | 1988-09-05 | High speed turbo pump |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0749798B2 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2008280125A (en) * | 2007-05-09 | 2008-11-20 | Akimasa Nozawa | Tape cutter |
-
1988
- 1988-09-05 JP JP22053388A patent/JPH0749798B2/en not_active Expired - Lifetime
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2008280125A (en) * | 2007-05-09 | 2008-11-20 | Akimasa Nozawa | Tape cutter |
Also Published As
Publication number | Publication date |
---|---|
JPH0749798B2 (en) | 1995-05-31 |
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