JPS5885368A - Hydraulic machine - Google Patents
Hydraulic machineInfo
- Publication number
- JPS5885368A JPS5885368A JP56181069A JP18106981A JPS5885368A JP S5885368 A JPS5885368 A JP S5885368A JP 56181069 A JP56181069 A JP 56181069A JP 18106981 A JP18106981 A JP 18106981A JP S5885368 A JPS5885368 A JP S5885368A
- Authority
- JP
- Japan
- Prior art keywords
- impeller
- blades
- runner
- hydraulic
- hydraulic machine
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03B—MACHINES OR ENGINES FOR LIQUIDS
- F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
- F03B3/02—Machines or engines of reaction type; Parts or details peculiar thereto with radial flow at high-pressure side and axial flow at low-pressure side of rotors, e.g. Francis turbines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03B—MACHINES OR ENGINES FOR LIQUIDS
- F03B11/00—Parts or details not provided for in, or of interest apart from, the preceding groups, e.g. wear-protection couplings, between turbine and generator
- F03B11/04—Parts or details not provided for in, or of interest apart from, the preceding groups, e.g. wear-protection couplings, between turbine and generator for diminishing cavitation or vibration, e.g. balancing
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Hydraulic Turbines (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は、振動強度の信頼性を高め主慎の小形化、＾連
化を達成する７ランシス形ポンプ水車および遠心ポンプ
轡の水力機械に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydraulic machine including a 7-run system pump-turbine and a centrifugal pump shoe, which improve the reliability of vibration strength and achieve downsizing and interconnection of the main shaft.
第１図４二上記水力機械の代表例であるフランシス形ボ
／ブ水車を示す。図において、符号１は回転軸を示し、
この回転軸１の下端区二羽根車２が固着され、この羽根
車２はハブ２ｍ＋ シュラウドリング２ｂおよび複数の
羽＄ ２ ｃとで形成されている。一方羽根車２の外周
側の固定流路には複数の案内羽＄３が円周方向（−等配
に配列され、水車運転時（Ｔ方向）には案内羽根３から
羽根車２、ポンプ運転時（Ｐ方向）４二は羽根車２から
案内羽根３へ流れを効率良く導くように形成されている
。FIG. 142 shows a Francis-type bob/bob water turbine, which is a typical example of the above-mentioned hydraulic machine. In the figure, numeral 1 indicates the rotation axis,
A two-impeller 2 at the lower end of the rotating shaft 1 is fixed, and the impeller 2 is formed of a hub 2m, a shroud ring 2b, and a plurality of blades $2c. On the other hand, a plurality of guide vanes $3 are arranged in the fixed flow path on the outer circumferential side of the impeller 2 in the circumferential direction (-equally spaced). The time (P direction) 42 is formed to efficiently guide the flow from the impeller 2 to the guide vanes 3.
ここで、羽根車の羽根枚数Ｚｒと案内羽根の羽根枚数Ｚ
ｇは従来性能面と構造上の容易性の観点から適切（二撰
定ｌされていた。しかし、最近のポンプ水車６：代表さ
れるごとく、経済性の面から主機の高格差化、高速化が
著しく、羽根車と案内羽根間の水圧脈動（二起因し九相
互干渉現象が羽根車の振動強度４＝与える影響度が着し
く増大し、このような厳しい使用条件工区；おける羽根
車の振、勲強度の信頼性をいかく二して向上させるがが
最近の解決すべき昧題としてクローズアップされている
。Here, the number of blades of the impeller Zr and the number of blades of the guide blade Z
Conventionally, g was appropriate from the viewpoint of performance and ease of construction. The influence of the water pressure pulsation between the impeller and the guide vanes (due to mutual interference phenomenon) steadily increases, and the vibration of the impeller in construction areas with such severe operating conditions increases considerably. However, how to improve the reliability of the strength of the engine has recently been highlighted as a problem that needs to be solved.
羽根車に作用する水力的加振力を説明する。水車運転時
、案内羽根３からの流水は案内羽根に発生した後流によ
り円周方向５二案内羽根の枚数分に相当する周期的（＝
変動する流れとなる。したがっ゛Ｃ１羽根車のに番目の
羽根（２Ｃ’ｋ）に層目した場合、回転中にＺｇ回の変
動する水力的加振力な受Ｖ−）、その周波数（／ｈ）は
容易（二
／ｈ ＝ Ｎ−Ｚｇ／６０ （Ｈｚ） ’
（１）となることが判る。また２（−ｃ以外の羽根は２
Ｃｋの羽根４二対しある位相遅れをもって同様の水力を
受け、羽根車全体としてはある位相差をもった複数の加
振力による振動現象が生ずる。The hydraulic excitation force acting on the impeller will be explained. During operation of the water turbine, the water flowing from the guide vanes 3 flows periodically (=
It becomes a fluctuating flow. Therefore, if the second blade (2C'k) of the C1 impeller receives a hydraulic excitation force V-) that fluctuates Zg times during rotation, its frequency (/h) is easily /h = N-Zg/60 (Hz)'
It turns out that (1) is obtained. Also, 2 (feathers other than -c are 2
The Ck blades 42 receive a similar hydraulic force with a certain phase lag, and a vibration phenomenon occurs in the impeller as a whole due to a plurality of excitation forces with a certain phase difference.
一方羽根車自体の固有振動上−ドは円板のヒ径モードＣ
二よって特徴づけられることが実験によって検証されて
いる。すなわち第２図に一例を示すが、直径モ−ド数（
１）がこのものは周方向に山（＋）と谷（→がそれぞれ
２個発生するモードである。従来の水力機械（＝あって
は、これ等直径モード数を有する羽根車の固有振動数は
式（１）の水力加振力周波数より高いとζろにあり、両
振動数が一致して共振するという現象は発生しない条件
１＝あった。On the other hand, the natural vibration of the impeller itself is the disk's radius mode C.
It has been experimentally verified that it is characterized by two characteristics. In other words, as an example is shown in Fig. 2, the diameter mode number (
1) is a mode in which two peaks (+) and two valleys (→) occur in the circumferential direction.In a conventional hydraulic machine (= the natural frequency of an impeller with equal diameter mode numbers) is higher than the frequency of the hydraulic excitation force in equation (1), and there is a condition 1 = that the phenomenon of both frequencies matching and resonating does not occur.
しかし前述の経済性ζ；よる小形高速機の採用が広く行
われるよう（＝なると、上記振動数の一致による共振現
象の危険性が問題となってきている。However, as the adoption of small high-speed machines based on the above-mentioned economy ζ becomes widespread, the danger of resonance due to the coincidence of the frequencies becomes a problem.
本発明は、この共振条件が発生し九としても前述の水力
加振力の多点加振の現象を適切（二制御することによっ
て羽根車６；発生する振動応力を著しく低下させ、強度
（３）での信頼性を著しく向上させた水力機械を提供す
ることを目的とする。The present invention significantly reduces the vibration stress generated by the impeller 6 by appropriately controlling the phenomenon of multi-point excitation of the hydraulic excitation force described above, even if this resonance condition occurs. ) The purpose is to provide a hydraulic machine with significantly improved reliability.
以下本発明について説明する。水力加振力の高調渡分も
考慮して、式（１）を変形すると、ω＝ｎ−Ｚｇ・Ω
（２）
となる。ここでΩ＝ Ｎ１５Ｑ 、 ｎは加振力の高
調波成分でｎ”Ｌ２＋・・・・・・の整数値、ωは加振
力の振動数である。耐３図にＺｒ＝６． Ｚｇ＝２０の
組合せの場合の配に図を示すが、ここでに１１目の羽根
（２Ｃｋ）の位置へとｉｉ４目の案内羽根（３１）の位
置θ直がすれ違は、羽根車上の任意の角度ψと任意時刻
ｔで、ｚ＋ｃ＝ ａ ｃｏｓｆ （ｇ＋−ｇ＞ｋ）ｓｉ
ｎａ＋（ｔ −（θｔ−９）ｋ） ） （３）Ω
と示せる。ここでａは振巾、ｅは直径節モード、ψにと
θＩは、以下のものを示′ＴＯ
（ｋ番目の羽根位置を回転系で示す。）羽根車に配列さ
れたに番目の羽根以外の羽根が受ける振動変位は式（３
）と同様（＝導かれ、全体としてはＺ「個の和として式
（４）のごとく示せるＯ＋島（・・ｌΩ））〕−
ＺｒΩ
式（２） 、 （４）のＷを考えると、振動変位２が励
振される条件として、
ω；ｌΩ＝ ｍ Ｚｒ８ （５）が得
られる。ここでｍは任意の整数である。すなわち、式（
２）（二よる加振力の強制振動数ωと羽根車の羽根枚数
Ｚｒが式（５）を満足するとき、羽根車の振動が励振さ
れる。他の振動数（二よる振動は各羽根位置からの振動
が互（二打消し合って、振動が励振されない。式（５）
に式（２）を代入し、Ωで両辺を割ると
ｎＺｇ ＋’ ／ ＝ ｍＺｒ
（６１ｆなわち式（６）を満足しないよう（＝Ｚｒ、Ｚ
Ｈの組合せを考えれビよい。The present invention will be explained below. If we transform equation (1) by taking into account the harmonic distribution of the hydraulic excitation force, we get ω=n−Zg・Ω
(2) becomes. Here, Ω = N15Q, n is the harmonic component of the excitation force and is an integer value of n''L2+..., ω is the frequency of the excitation force. Zr = 6. Zg = The diagram shows the arrangement for 20 combinations. Here, the position of the 11th blade (2Ck) and the position θ of the 4th guide blade (31) are different from each other because of any arbitrary position on the impeller. At angle ψ and arbitrary time t, z+c= a cosf (g+-g>k)si
It can be shown as na+(t-(θt-9)k)) (3)Ω. Here, a is the amplitude, e is the diameter nodal mode, and ψ and θI are the following.'TO (The position of the k-th blade is shown in the rotation system.) Other than the 2-th blade arranged in the impeller. The vibration displacement received by the blade is expressed by the formula (3
) (= derived, and as a whole Z ``O+ island (...lΩ) which can be shown as the sum of the pieces as in equation (4))] - ZrΩ Considering W in equations (2) and (4), vibration As a condition for the displacement 2 to be excited, ω;lΩ=m Zr8 (5) is obtained. Here, m is an arbitrary integer. That is, the formula (
2) When the forced frequency ω of the excitation force due to two (2) and the number of blades Zr of the impeller satisfy equation (5), the vibration of the impeller is excited. The vibrations from the position cancel each other out and the vibrations are not excited.Equation (5)
Substituting equation (2) into and dividing both sides by Ω, we get nZg +' / = mZr
(61f, that is, formula (6) is not satisfied (=Zr, Z
Let's think about the combination of H.
一般（＝、増力機械の場合、水中での減衰が大きく、ｎ
＝１の基本振動加振力を考慮すれば十分であり、実測結
果（＝よっても検証され工いる、。ま九羽根車の固有振
動モードとしてはｎ＝２．３．４ 直径節の固有振動
数が加振力の振動数と一致し易い条件にあシ、この範囲
をさければ十分である。さらにＺｒ、Ｚｇｌ：ｌ一つい
ては性能および構造、製作上のＺｒ＝５〜９の整数
Ｚｇ ＝ ７〜３２ （７）整ｔｊ！、 （但Ｌ Ｚ
ｇ＞Ｚｒ＋１）に制限される。よって、以下の組合せが
式（６）を満足しない条件として撰定される。General (=, in the case of a booster machine, the attenuation in water is large, n
It is sufficient to consider the basic vibration excitation force of = 1, and the actual measurement result (= is also verified.) The natural vibration mode of the nine impeller is n = 2.3.4 The natural vibration of the diameter node If the number easily matches the frequency of the excitation force, it is sufficient to avoid this range.Furthermore, Zr, Zgl: In terms of performance, structure, and manufacturing, Zr = an integer of 5 to 9, Zg. = 7~32 (7) Set tj!, (However, L Z
g>Zr+1). Therefore, the following combinations are selected as conditions that do not satisfy equation (6).
Ｚｒ−５（７，）とき ｚｇ＝ １０．１５，１６，２
０，２４，２５，３０゜Ｚｒ＝６（７）とき Ｚｇ＝１
１，１２，１３，１７．１８，１９．２３．２４２５
、２９．３０
ｚｒニアのとき Ｚｇ＝ＩＯ，１３，１４，１５，２０
，２１，２２，２７９
Ｚｒ＝８１７）と！ Ｚｇ＝１５．１６．１７，１８
．２３，２４，２５．３１２
Ｚｒ＝９のとき Ｚｇ＝１７．１８，１９．２６，２７
．２８ＺｒとＺｇの組合せは主機の運転仕様（＝よって
左右される面があり、−例として、ポンプ水車の縦近の
仕様の変化を第４図Ｃ二示す。第４図で横軸はＮ５＝Ｎ
ＪＱＡ１ｐ％で定義されるポンプ比速度で、Ｑ・ｆ（ｐ
はポンプ最高＃ｈ程運転時の流〜蓋および揚程である。When Zr-5 (7,), zg= 10.15, 16, 2
0, 24, 25, 30° When Zr=6(7) Zg=1
1, 12, 13, 17.18, 19.23.2425
, 29.30 When zr near Zg=IO, 13, 14, 15, 20
, 21, 22, 279 Zr=817)! Zg=15.16.17,18
．． 23, 24, 25.312 When Zr=9 Zg=17.18, 19.26, 27
．． 28 The combination of Zr and Zg is influenced in some ways by the operating specifications of the main engine. As an example, changes in the vertical and near specifications of a pump-turbine are shown in Figure 4 C2. In Figure 4, the horizontal axis is N5 = N
At the pump specific speed defined as JQA1p%, Q・f(p
are the flow to lid and lift when the pump is operated at maximum #h.
またｋはに＝ＮＪＱで定義される機器の高速化を示す係
数である。第４図より年々高＃ｒ差、高速化が計られて
いることが判る。（○印は実用化中のもの、◇印は計画
中のものである。）最近はｎ ｓ ＝２０〜４５ ｍ−
ｍ□ｓ 、 Ｈｐ ＞ ３００の範囲（二開発が集中し
ておシ、この範囲ではＺｒ＝５〜７が性能上より撰ｄれ
る。これより高比速度側ではＺｒ＝７〜９が適切な羽根
枚数となる。Further, k is a coefficient indicating the speedup of the device defined by ni=NJQ. From Figure 4, it can be seen that the difference in height #r and the speed increase are being achieved year by year. (○ marks are those in practical use, ◇ marks are under planning.) Recently, n s = 20 to 45 m-
m□s, Hp > 300 range (Two developments are concentrated, and in this range Zr = 5 to 7 is selected from the viewpoint of performance. On the higher specific speed side, Zr = 7 to 9 is appropriate. The number of blades.
また第４図より低比速度程ｋを大きくする傾向にある示
、これは以下の理由による。Furthermore, FIG. 4 shows that k tends to increase as the specific speed decreases, and this is due to the following reasons.
（１） 低比速度水力機械では、第５図に示すランナ
人口中伸）とランチ外径（Ｄｏ）の比Ｂ／Ｄｏが相対的
（二小さくなり、ランチ内部の羽根２Ｃの形状を仕上げ
ることが難かしくなる。そこでｋを大きくして、高比速
度形の形状（Ｂが大きくなる）にすることが製作上の容
易性から望ましい０
（２）低比速度水力機械では、ＪＩｓ図のＤｏ／Ｄｅの
比が大きくなり、羽根車外径ＤＯの寸法が大きくなって
、一体での輸送が難かしく、大容量化する場合のネック
となる。(1) In a low specific speed hydraulic machine, the ratio B/Do of the runner population growth (as shown in Fig. 5) and the launch outer diameter (Do) becomes relatively (2) smaller, and the shape of the vane 2C inside the launch can be finished. Therefore, it is desirable to increase k and create a high specific speed shape (B becomes large) from the viewpoint of manufacturing ease. (2) For low specific speed hydraulic machines, Do of the JIs diagram /De becomes large, and the impeller outer diameter DO becomes large, making it difficult to transport the impeller in one piece, which becomes a bottleneck in increasing the capacity.
（３） ｌ）ｏ／Ｄｅの比が大きくなることはノ・プ
２ｍ、と上カバ４、シュラウドリンク２ｂと下カッ（５
の曲の円ｆｍ摩Ｓ損失が増大し、効率が忌倣に低−ト「
る。(3) l) An increase in the o/De ratio means that No. 2 m, upper cover 4, shroud link 2b and lower cup (5
The circle fm friction S loss of the song increases, and the efficiency becomes extremely low.
Ru.
そこＣ高効率化を計るうえで、高比速度形鴫＝するのが
望ましい。Therefore, in order to achieve high efficiency, it is desirable to use a high specific speed type.
しかし高比速度化を計ると、一般（二羽根車の剛性が低
下して、羽根車の固有振動数が低下する。However, when increasing the specific speed, the rigidity of the two-impeller generally decreases, and the natural frequency of the impeller decreases.
一方式（１）から判るごとく、高速化（＝よって水力加
振力の周波数は増加して、羽根車の固有振動数との一致
による共振現象が発生する危険性を有している。（１、
＝＝ ３０ ｍ ｍ”／１％のポンプ水車（二ついて計
算した試算例を第６図に示す。第４図に示ずに＝ ２５
００の現状の羽根車では、第６図の０点にあシ、水力加
振力周波数（／ｈａ） （：対し、羽根車の固有振ｗＪ
ａ（／ｎ）は十分離れてお９安全ｌｌｌ （二ある。し
かし、同一落差してｎａを上げて高速化を計ると第６図
に示すごとく０点（二て両Ｆｉ動数が一致して共振現象
ｔ−発生する危険性がある。On the other hand, as can be seen from equation (1), the frequency of the hydraulic excitation force increases as the speed increases (= therefore, there is a risk that a resonance phenomenon will occur due to coincidence with the natural frequency of the impeller. (1) ,
== 30 mm"/1% pump-turbine (Figure 6 shows an example of calculation using two pump turbines. Not shown in Figure 4 = 25
For the current impeller of 00, the hydraulic excitation force frequency (/ha) is at the 0 point in Figure 6, whereas the natural vibration of the impeller wJ
a(/n) is sufficiently far apart to be safe at 9 (2). However, if you try to increase the speed by increasing na with the same head, as shown in Figure 6, it will be 0 point (2). There is a risk that a resonance phenomenon will occur.
一方案内羽根の枚数は構造上、据付上の容易性から偶数
を採用することが望ましく ｓ ”ｓ＜４５の範囲４二
あるフランシス形ポンプ水車では芙用面を考慮して、Ｚ
ｒとＺｇ （二関し下記の組合せが撰ばれる。On the other hand, it is desirable to adopt an even number of guide vanes from the viewpoint of ease of construction and installation.
r and Zg (The following combinations are selected.
’ｔｒ＝５ ： Ｚｇ＝１０＃１６ｔ２０＃２４ｚ
ｒ＝ ６ ： Ｚｇ−＝ １２−ＩＬ２４Ｚｒ＝
７ ： Ｚｇ＝ １０．１４−２０＊２２また、遠
心ポンプとしては案内羽根ζ二固定羽根を使用する例が
多く、ｚｇは奇数を用いることもあり、また相対的（”
−Ｚｇの枚数は少い。そこで、以下の組合せを用いるこ
とが好ましい。'tr=5: Zg=10#16t20#24z
r= 6: Zg-= 12-IL24Zr=
7: Zg = 10.14-20*22 In addition, in many cases, centrifugal pumps use two fixed guide vanes, zg is sometimes an odd number, and relative (
-The number of Zg sheets is small. Therefore, it is preferable to use the following combinations.
１ｒ＝５ ： ｚｇ＝１０ｔｌＬ１Ｇ
Ｚｒ−＝６ ： Ｚｇ＝ １１．１２．１３Ｚｒ ＝
７ ： Ｚｇ＝ １０．１３．１４．１５Ｚｒ ＝８
： Ｚｇ＝ １５．１６−１７．１８Ｚｒ＝ ９ ：
Ｚｇ＝ １７．１８．１９以上述べたごとく本発明は今
後増々高＃ｒ差、高速化する水力機械の羽根車の振動強
度面での問題点を解決し、信頼性の高い一体ランチでの
大容量化、性能向上による省エネルギー面での効果、小
形化ζ二よる経済的効果等数々′のメリットを発揮しう
る機器を信頼性をそこなうこと磨く提供しうる効果を有
している。1r=5: zg=10tlL1G Zr-=6: Zg= 11.12.13Zr=
7: Zg=10.13.14.15Zr=8
: Zg= 15.16-17.18Zr= 9 :
Zg = 17.18.19 As mentioned above, the present invention solves problems in terms of the vibration strength of impellers of hydraulic machines, which will continue to increase in height #r difference and speed, and provides a highly reliable integrated launch with a large It has the effect of improving the reliability of equipment, which can exhibit a number of advantages, such as energy saving effects due to increased capacity and improved performance, and economical effects due to miniaturization.
第１図は７ランシス形ポンプ水車を示す平面図および縦
断面図、第２図は羽根車の固有モードの代表例を示す説
明図、第３図は多点加振境象の説明図、第４図は最近の
７ランシス形ポンプ水車の適用範囲を示す特性−１第５
図は水力機械の部分断面図、第６図は水力加振周波数と
羽根車固南振動数との関係を示す線図である。
１・・・回転軸 ２・・・羽根車２Ｆ・ハブ
２ｂ、・・シュラウド２ｃｍ・・羽根リング
３・・案内羽根４・・・上カバ ５川下
カバ
（７３１７） 代理人 弁理士 則 近 憲 佑 （
はが１名）第１図
第２図
第３図Figure 1 is a plan view and longitudinal cross-sectional view showing a 7 Lances type pump-turbine, Figure 2 is an explanatory diagram showing a typical example of the eigenmode of the impeller, Figure 3 is an explanatory diagram of a multi-point vibration situation, Figure 4 shows the applicable range of recent 7 Lances type pump turbines.
The figure is a partial cross-sectional view of the hydraulic machine, and FIG. 6 is a diagram showing the relationship between the hydraulic excitation frequency and the impeller Oscillation frequency. 1... Rotating shaft 2... Impeller 2F/hub
2b,... Shroud 2cm... Feather ring 3... Guide vane 4... Upper cover 5 Lower cover (7317) Agent: Kensuke Chika, patent attorney (7317)
(1 person) Figure 1 Figure 2 Figure 3
Claims (1)
よびシュラウドリングとより形成される羽根車と、この
羽根車に隣設した固定流路側（二設けられた案内羽根と
を有するもの響二おいて、羽根車の羽根枚数をＺｒ、案
内羽根の枚数をＺｇとした場合、ＺｒとＺｇを夫々以下
に定める組合せのうちいずれか−の組合せ（−て設定し
九ことを特徴とする水力機械。 Ｚｒ＝５ ： Ｚｇ＝１０＋１５ｓｌｔｉｓ２０ｓ２４
＊２５＋３０’Ｌｒ＝６ ： ｚｇ−１１−１２−１３
−１７−１８−１９−２３−２４−２５４９−０ Ｚｒ＝７ ： Ｚｇ＝１０．１３，１４，１５．２０ｓ
２１．２２．−２７．２９Ｚｒ＝８ ： Ｚｇ”’１５
＋１６ｅ１７ｔｌＬ２３ｓ２４＊２５．３１ｅ３−２Ｚ
ｒ＝９ ： Ｚｇ＝１７１１８−１９＊２６−２Ｌ
２Ｂ（２） ポンプ最高揚程運転時の流量をＱ（□Ｓ
）、揚程を）ｉｐ（ｍ） 、回転数をＮ （ｒ、ｐ、ｍ
）としたとき、ポンプ比速度ｎｓ （＝ＮＪＱ／ＨＩ）
’ ）がｎｍ≦４５であり、かつ係数ｋ （＝ＮＪＱ）
かに≧３０００であり、８ ｂ ＋ニーＺｒとＺｇを夫
々以下に定める組合せのうちいずれか−の組合せにて設
定したフランシス形ポンプ水車であることを特徴とする
特許請求の範囲第１項記載の水力機械。 Ｚｒ＝＝５ ： Ｚｇ＝１０＋１６．２０＋２４Ｚｒ−
６： Ｚｇ＝１２．１８．２４ Ｚｒ＝７ 二 Ｚｇ＝１０．１４．２Ｑ、２２（３）
ｋａ３０００であり カッＺｒ （！： Ｚｇ を
夫ｈ 以下ニ定める組合せのうちいずれか−の組合せ（
二で設定した遠心ポンプであることを特徴とする特許請
求の範囲！１項記載の水力機械。 Ｚｒ ＝５ ： Ｚｇ＝１０．１５．１６Ｚｒ＝６ ：
Ｚｇ＝ＩＬ１２ｅ１３ Ｚｒ”’７ ： Ｚｇ＝１０．１３，１４．１５Ｚｒ＝
８ ： Ｚｇ＝１５．１６，１７．１８Ｚｒ＝９ ：
Ｚｇ＝１７．１８．１９[Claims] An impeller formed by (11 plural blades and a shroud ring surrounding the blades in the vertical direction), and a fixed flow path side (2 provided For Hibiki, which has a guide vane, if the number of blades of the impeller is Zr and the number of guide blades is Zg, then Zr and Zg are set by any one of the combinations specified below (-). A hydraulic machine characterized by nine things. Zr=5: Zg=10+15sltis20s24
*25+30'Lr=6: zg-11-12-13
-17-18-19-23-24-2549-0 Zr=7: Zg=10.13, 14, 15.20s
21.22. -27.29Zr=8: Zg"'15
+16e17tlL23s24*25.31e3-2Z
r=9: Zg=17118-19*26-2L
2B (2) The flow rate during pump maximum head operation is Q(□S
), the lifting height is )ip (m), and the number of revolutions is N (r, p, m
), pump specific speed ns (=NJQ/HI)
) is nm≦45, and coefficient k (=NJQ)
Crab≧3000, and the invention is a Francis-type pump-turbine in which 8 b + knee Zr and Zg are set to any one of the combinations set forth below. hydraulic machinery. Zr==5: Zg=10+16.20+24Zr-
6: Zg=12.18.24 Zr=7 2 Zg=10.14.2Q, 22(3)
ka3000 and Ka Zr (!: Zg as husband h) Any one of the combinations specified below (
Claims characterized in that it is a centrifugal pump set in two! The hydraulic machine described in item 1. Zr = 5: Zg = 10.15.16 Zr = 6:
Zg=IL12e13 Zr"'7: Zg=10.13, 14.15Zr=
8: Zg=15.16, 17.18Zr=9:
Zg=17.18.19
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP56181069A JPS5885368A (en) | 1981-11-13 | 1981-11-13 | Hydraulic machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP56181069A JPS5885368A (en) | 1981-11-13 | 1981-11-13 | Hydraulic machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5885368A true JPS5885368A (en) | 1983-05-21 |
| JPS6244099B2 JPS6244099B2 (en) | 1987-09-18 |
Family
ID=16094251
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP56181069A Granted JPS5885368A (en) | 1981-11-13 | 1981-11-13 | Hydraulic machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5885368A (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62182996U (en) * | 1986-05-12 | 1987-11-20 | ||
| JPS6385698U (en) * | 1986-11-20 | 1988-06-04 | ||
| JPS63145889U (en) * | 1987-03-17 | 1988-09-27 | ||
| JPH01207095A (en) * | 1988-02-15 | 1989-08-21 | Matsushita Electric Works Ltd | Hair cutting device provided with hair-scrap-containing section |
| JPH01207096A (en) * | 1988-02-15 | 1989-08-21 | Matsushita Electric Works Ltd | Hair cutting device provided with hair-scrap-containing section |
-
1981
- 1981-11-13 JP JP56181069A patent/JPS5885368A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6244099B2 (en) | 1987-09-18 |
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