CN102606368A - Calculating method for diameter of rotating wheel of reversible pump turbine - Google Patents

Abstract

The invention discloses a calculating method for the diameter of a rotating wheel of a reversible pump turbine. The calculating method can be used for calculating the diameter of a high-pressure side of the rotating wheel and the diameter of a low-pressure side of the rotating wheel, a simple calculating statistic formula for calculating the diameter of the rotating wheel of the reversible pump turbine is provided according to detailed research and analysis about correlations of diameters of rotating wheels of a plurality of pump turbines and parameters such as minimum head, minimum head flow, specific speed, rated output power of shafts of power generation motors, and the like. The calculating statistic formula for calculating the diameter of the rotating wheel of the reversible pump turbine provides the scientific and reasonable calculating method for the diameter of the rotating wheel of the reversible pump turbine, so that a designer can calculate and select the proper diameter of the rotating wheel without the aid of hydraulic model tests, labor and materials are saved, and efficiency is improved.

Description

The computational methods of Reversible Pump-Turbine runner diameter

Technical field

The present invention relates to a kind of computational methods of pump turbine runner diameter, especially a kind of computational methods of Reversible Pump-Turbine runner diameter.

Background technique

The calculating of Reversible Pump-Turbine runner diameter in the prior art mainly relies on unit model test or by confirming behind the water turbine operating mode pro form bill bit traffic again.

(1) confirms by model test:, choose suitable water turbine operating mode rated head specific discharge Q after taking all factors into consideration pump operating condition performance and water turbine performance of operating condition according to the collective model characteristic curve of same head/lift section pump turbine group ₁₁, again according to following formula pump turbine runner diameter:

$D_1={\left[\frac{N_r}{8.88\×Q_{11}\×H_r^{1.5}}\right]}^{0.5}$

Wherein: D ₁-runner high pressure side diameter (m);

N _r-water turbine operating mode rated power (kW);

H _r-water turbine operating mode rated head (m);

Q ₁₁Specific discharge (m under the-water turbine operating mode rated head ³/ s).

Lack limit below existing as stated above:

1) owing to limited by storage station's construction condition; Basically can't find the pump turbine group collective model characteristic curve of same head/lift; Need according to close head/lift pump turbine model through repairing type and behind overtesting, drawing new model generalization curve again; Investment increases greatly like this, and needs the cost model test time of nearly half a year.This method only is adapted to do the design of actual waterpower to the power station after producer submits a tender or gets the bid, and in the engineering feasibility study design, more numerous than selecting scheme, impossible employing the method.

2) this method can only be calculated runner high pressure side diameter, can not carry out runner low voltage side diameter and calculate.

(2) pressing water turbine operating mode pro form bill bit traffic calculates: according to the H of Fig. 1 _r-n _StStatistic curve is tentatively chosen the specific speed n under the water turbine operating mode rated head _St(mkW).H _rDuring>=400m, at K _tChoose n on=2400 curves _St400m＞H _rCan be during>=100m at K _tChoose n on=2200 curves _StH _rDuring＜100m at K _t=2000 or K _tChoose n on=1800 curves _St, be calculated as follows runner diameter again:

Q ₁₁＝0.003×n _st-0.15

$D_1={\left[\frac{N_r}{8.88\×Q_{11}\×H_r^{1.5}}\right]}^{0.5}$

Above-mentioned: n _StBe the specific speed (mkW) under the water turbine operating mode rated head;

K _tBe the coefficient of specific speed under the water turbine operating mode rated head.

Calculate by this method, have following shortcoming:

1) chooses the specific speed under the water turbine operating mode rated head on coefficient of specific speed's curve of these computational methods according to the different head sections of statistics; Rated head adopts same statistic curve within the specific limits on the one hand, exists than mistake, on the other hand; Actual conditions show the pump turbine of same capability and same nominal head; If minimum lift is different, it is bigger that its runner diameter will differ, will be the same and calculate its result as stated above; Existence is than mistake, and is inaccurate, impracticable when the actual design scheme compares.

2) this method is by water turbine condition calculating runner diameter purely; And the pumped storage power station pump operating condition is more complicated than the water turbine operating mode; Generally press the pump operating condition design, promptly preferentially guarantee the pump operating condition performance, as calculating as stated above; Generally be difficult to guarantee the pump operating condition performance, the diameter that calculates can not finely satisfy the pump operating condition requirement.

Summary of the invention

Technical problem to be solved by this invention is that providing a kind of is support with actual engineering data, the computational methods of the Reversible Pump-Turbine runner diameter that method is simple, easy to use.

In order to solve the problems of the technologies described above, the technological scheme that the present invention adopts is: a kind of computational methods of Reversible Pump-Turbine runner diameter may further comprise the steps:

(1) calculates minimum lift flow

according to the engineering actual parameter

Wherein, H _PminBe the minimum lift of Reversible Pump-Turbine, m;

Q _PminBe the minimum lift flow of Reversible Pump-Turbine, m ³/ s;

N _rBe reversible generator motor nominal axes output power, kW;

G is a gravity accleration, m/s ²

η _pBe the minimum lift efficient of Reversible Pump-Turbine, %;

(2) calculate the minimum lift specific speed of pump turbine,

Wherein, n _rBe pump turbine rated speed, r/min;

(3) calculate pump turbine high pressure side runner diameter:

$D_1=\frac{(0.3504\×n_{\mathrm{sp}}+75.75)\×\sqrt{H_{p\min }}}{n_r}$

Or

K wherein ₁=0.3504 * n _Sp+ 75.75;

(4) calculate pump turbine low voltage side runner diameter:

D ₂＝(0.006×n _sp+0.3184)×D ₁

Or D ₂=K ₂* D ₁

K ₂＝0.006×n _sp+0.3184。

Said Reversible Pump-Turbine is that single-stage is decided rotating speed mixed flow Reversible Pump-Turbine.

The invention has the beneficial effects as follows: pump turbine runner diameter formula of the present invention comprises runner high pressure side diameter and low voltage side diameter; Runner diameter through a plurality of pump turbines and minimum lift, minimum lift flow, specific speed and the isoparametric correlation of generator motor nominal axes output power study analysis in great detail, the statistical formula that a kind of simple computation Reversible Pump-Turbine runner diameter calculates is proposed.Described Reversible Pump-Turbine runner formula provides scientific and reasonable pump turbine runner diameter computational methods; The artificer can be calculated on need not through the basis of hydraulic model test; This calculating is simultaneously calculated from pump operating condition; Guarantee the pump operating condition performance, thereby saved on the basis of human and material resources more accurately, improved efficient.

Description of drawings

Fig. 1 is the H that existing technology is calculated by water turbine operating mode pro form bill bit traffic _r-n _StStatistic curve;

Fig. 2 is K in the diameter computational methods of Reversible Pump-Turbine runner of the present invention high pressure side ₁The minimum lift specific speed of value coefficient and water pump n _SpGraph of relation;

Fig. 3 is K in the Reversible Pump-Turbine runner low voltage side diameter computational methods of the present invention ₂The minimum lift specific speed of value coefficient and water pump n _SpGraph of relation.

Embodiment

Below in conjunction with accompanying drawing and embodiment the present invention is done further explain:

The computational methods of Reversible Pump-Turbine runner diameter of the present invention may further comprise the steps:

(1) calculates minimum lift flow according to the engineering actual parameter

Wherein, H _PminBe the minimum lift of Reversible Pump-Turbine, m;

Q _PminBe the minimum lift flow of Reversible Pump-Turbine, m ³/ s;

N _rBe reversible generator motor nominal axes output power, kW;

G is a gravity accleration, m/s ²

η _pBe the minimum lift efficient of Reversible Pump-Turbine, %;

(2) calculate the minimum lift specific speed of pump turbine,

Wherein, n _rBe pump turbine rated speed, r/min;

(3) calculate pump turbine high pressure side runner diameter:

$D_1=\frac{(0.3504\×n_{\mathrm{sp}}+75.75)\×\sqrt{H_{p\min }}}{n_r}$

Or

K wherein ₁=0.3504 * n _Sp+ 75.75;

(4) calculate pump turbine low voltage side runner diameter:

D ₂＝(0.006×n _sp+0.3184)×D ₁

Or D ₂=K ₂* D ₁

K ₂＝0.006×n _sp+0.3184。

Said Reversible Pump-Turbine is a single-stage mixed flow pump water turbine.

Specifically, Reversible Pump-Turbine runner diameter computational methods formula of the present invention:

$D_1=\frac{(0.3504\×n_{\mathrm{sp}}+75.75)\×\sqrt{H_{p\min }}}{n_r}$

Or $D_1=\frac{K_1\sqrt{H_{p\mathrm{Min}}}}{n_r}$

K ₁＝0.3504×n _sp+75.75；

D ₂＝(0.006×n _sp+0.3184)×D ₁

Or D ₂=K ₂* D ₁

K ₂＝0.006×n _sp+0.3184。

Obtain through following approximating method: the relation according to building of listing in the table 1, project under construction Reversible Pump-Turbine runner high pressure side diameter and minimum lift and rated speed simulates K ₁-n _SpPlotted curve, as shown in Figure 2, fit to formula and be:

K ₁＝0.3504×n _sp+75.75

Relation according to building of listing in the table, project under construction Reversible Pump-Turbine runner low voltage side diameter and runner high pressure side runner diameter and minimum lift specific speed simulates K ₂-n _SpPlotted curve, as shown in Figure 3, fit to formula and be:

K ₂＝0.006×n _sp+0.3184

Table 1 has been built pumped storage power station runner diameter and minimum lift, minimum lift flow and specific speed relation table

The power station title	H pmin	Q pmin	n r	n sp	D 1	D 2	K 1	D 1Calculated value	K 2	D 2Calculated value
											Ohira	509	45	400	25.04	4.78	2.18	84.748	4.77	0.469	2.24
chaira	613.4	29.5	600	26.44	3.52	1.638	85.275	3.51	0.477	1.67
											S.jares	235	10.1	500	26.47	2.46	1.2	80.236	2.61	0.477	1.24
Hongawa	532.1	54.31	400	26.61	4.9	2.346	84.969	4.91	0.478	2.35
											Numapara	458	50	375	26.78	4.95	2.64	86.737	4.86	0.479	2.33
Bajna?Basta	531.7	50.8	428.6	27.59	4.828	2.18	89.74	4.6	0.484	2.23
											Chongpyong	474	39	450	27.66	4.055	1.868	83.814	4.13	0.484	2
Okukiyotsu	461	54	375	27.7	5.2	0	90.821	4.89	0.485	2.37
											Taumsauk	233	75	200	29.04	6.475	3.239	84.838	6.56	0.493	3.23
Tamhara	505.1	52.5	428.6	29.15	4.53	2.25	86.39	4.51	0.493	2.22
											Cabin?creek	319	39	360	29.78	4.191	2.061	84.474	4.28	0.497	2.13
Imaichi	528	59.3	428.6	29.96	4.62	2.258	86.174	4.62	0.498	2.3
											Drskensburg	420.5	58.1	375	30.78	4.72	2.316	86.316	4.73	0.503	2.38
Okutataragi	366.8	76.7	300	31.35	5.638	2.8	88.314	5.54	0.507	2.81
											Helms	450	74	360	31.7	5.3	0	89.944	5.12	0.509	2.61
Okuyoshjno	468	39.4	514.3	32.08	3.76	1.834	89.388	3.66	0.511	1.87
											Shimogo	392	62	375	33.52	4.61	2.47	87.315	4.62	0.52	2.4
It waste level ground	532	57.7	500	34.29	4.08	2.045	88.445	4.05	0.524	2.12

The power station title	H pmin	Q pmin	n r	n sp	D 1	D 2	K 1	D 1Calculated value	K 2	D 2Calculated value
											The Ming Tombs	440.4	43.5	500	34.3	3.6311	1.949	86.514	3.68	0.524	1.93
Huhehaote	507.6	55.27	500	34.76	3.88	1.911	86.107	3.96	0.527	2.09
											Extensively hold the second phase	514	57.3	500	35.06	3.802	2.09	83.85	3.99	0.529	2.11
Kinorwic	500	55.5	500	35.23	3.796	2.03	84.881	3.94	0.53	2.09
											Montezic	388	51.9	428.6	35.32	4.01	0	87.253	4.05	0.53	2.15
Bath?County	334	116	257.1	35.44	6.349	3.355	89.317	6.27	0.531	3.33
											Extensively hold first phase	514	60	500	35.88	3.886	2.312	85.702	4	0.534	2.14
Mosul?II	321.4	31.23	500	36.81	3.13	0	87.295	3.18	0.539	1.71
											Prozelton	285	26.3	500	36.97	3.01	1.616	89.149	3	0.54	1.62
Castaic	265	91	257.1	37.34	5.84	0	92.234	5.62	0.542	3.05
											Yixing	360	69.5	375	37.83	4.38	2.6	86.567	4.5	0.545	2.45
Nabara	280.5	110	257	39.33	5.95	3.3	91.303	5.83	0.554	3.23
											The small stream mouth	242	17.3	600	40.67	2.248	1.332	86.704	2.33	0.562	1.31
Anapo	292.1	45.5	428.6	40.92	3.575	0	89.653	3.59	0.564	2.02
											Shin	229.6	128.1	214.3	41.12	6.35	3.87	89.807	6.37	0.565	3.6
Coo?II	235	82.4	273	41.29	5.26	2.823	93.673	5.07	0.566	2.87
											Bright pool	357.2	72.3	400	41.39	4.3	0	91.007	4.26	0.567	2.42
Rodund?II	324	71.5	375	41.52	4.328	2.424	90.167	4.33	0.568	2.46
											Open the river bend	295.75	80.25	333.3	41.87	4.61	2.665	89.346	4.67	0.57	2.66
Pu Shihe	294.37	101.05	300	42.43	5.2	0	90.924	5.18	0.573	2.97
											Viandeno	267	74.1	333	43.4	4.39	2.446	89.465	4.46	0.579	2.58
Kisenyama	197	110	225	44.88	5.7	3.38	91.374	5.71	0.588	3.36
											Revin	212	69.2	300	44.92	4.33	2.72	89.216	4.44	0.588	2.61
Black elk peak	276.2	106	300	45.59	5.15	2.83	92.964	5.08	0.592	3.01
											Mloty	248.8	96.5	300	47.04	4.94	3.25	93.956	4.85	0.601	2.91
Raccoonmt	287	127	300	48.49	4.926	3.302	87.232	5.24	0.609	3.19
											Robiei	285	11.8	1000	49.52	1.65	1	97.738	1.57	0.616	0.97
Bear-swamp	209	155	225	50.96	5.84	0	90.891	6.01	0.624	3.75
											Tongbai	237.54	119.3	300	54.16	4.802	3.154	93.471	4.87	0.643	3.13
Tai'an	223.58	112.36	300	55	4.548	3.012	91.248	4.74	0.648	3.07
											Ravine, Xiangshui County	178.94	137.35	250	59.89	5.139	3.28	96.043	5.18	0.649	3.51
Shin?toyone1#5#	180	122.9	250	56.4	5.42	3.525	101	5.13	0.657	3.37
											Shin?toyone2#4#	180	122.9	257	57.98	5.42	3.525	103.82	5.02	0.666	3.34
Juktan	199	109.8	300	59.33	4.588	3.1	97.57	4.54	0.674	3.06
											The white lotus river	191	151.3	250	59.85	5.177	3.315	93.649	5.35	0.678	3.63
The Mt. Langya	124.7	123.6	230.8	68.76	4.725	3.336	97.657	4.83	0.731	3.53

Checking computations embodiment is following:

Embodiment 1

If the minimum lift H of known pumped storage power station _PminBe 295.13m, generator motor nominal axes output power 268MW, rated speed is 333.3r/min, the minimum lift efficient 92% of pump turbine is calculated the pump turbine runner diameter.

The first step: calculate minimum lift flow Q according to the engineering actual parameter _Pmin:

$Q_{p\min }=\frac{0.97\×N_r\×{\mathrm{\η}}_p}{g\×H_{p\min }}$

$=\frac{0.97\×268\×1000\×0.92}{9.81\×295.13}$

$=82.6(m^3/s)$

Wherein,

H _PminBe the minimum lift (m) of Reversible Pump-Turbine;

Q _PminBe the minimum lift flow of Reversible Pump-Turbine (m ³/ s);

N _rBe reversible generator motor nominal axes output power (kW);

G is gravity accleration (m/s ²);

η _pBe the minimum lift efficient (%) of Reversible Pump-Turbine

Second step: calculate the minimum lift specific speed of pump turbine n _Sp:

$n_{\mathrm{sp}}=\frac{n_r\sqrt{Q_{p\min }}}{{H_{p\min }}^{0.75}}$

$=\frac{333.3\×\sqrt{82.6}}{{295.13}^{0.75}}$

$=42.54(m-m^3/s)$

The 3rd step: calculate pump turbine high pressure side runner diameter:

$D_1=\frac{(0.3504\×n_{\mathrm{sp}}+75.75)\×\sqrt{H_{p\min }}}{n_r}$

$=\frac{(0.3504\×42.54+75.75)\×\sqrt{295.13}}{333.3}$

$=4.673\left(m\right)$

The 4th step: calculate pump turbine low voltage side runner diameter:

D ₂＝(0.006×n _sp+0.3184)×D ₁

＝(0.006×42.54+0.3184)×4.673

＝2.68(m)

It is for reference to list employing empirical correlation result calculated of the present invention and test result in the table 1.

Above-described embodiment only is used to explain technological thought of the present invention and characteristics; Its purpose is to make those skilled in the art can understand content of the present invention and implements according to this; Can not only limit claim of the present invention with present embodiment; Be equal variation or the modification that all disclosed spirit is done, still drop in the claim of the present invention.

Claims (2)

1. the computational methods of a Reversible Pump-Turbine runner diameter is characterized in that, may further comprise the steps:

(1) calculates minimum lift flow

according to the engineering actual parameter

Wherein, H _PminBe the minimum lift of Reversible Pump-Turbine, m;

Q _PminBe the minimum lift flow of Reversible Pump-Turbine, m ³/ s;

N _rBe reversible generator motor nominal axes output power, kW;

G is a gravity accleration, m/s ²

η _pBe the minimum lift efficient of Reversible Pump-Turbine, %;

(2) calculate the minimum lift specific speed of pump turbine,

Wherein, n _rBe pump turbine rated speed, r/min;

(3) calculate pump turbine high pressure side runner diameter:

$D_1=\frac{(0.3504\×n_{\mathrm{sp}}+75.75)\×\sqrt{H_{p\min }}}{n_r}$

Or

K wherein ₁=0.3504 * n _Sp+ 75.75;

(4) calculate pump turbine low voltage side runner diameter:

D ₂＝(0.006×n _sp+0.3184)×D ₁

Or D ₂=K ₂* D ₁

K ₂＝0.006×n _sp+0.3184。

2. the computational methods of Reversible Pump-Turbine runner diameter according to claim 1 is characterized in that, said Reversible Pump-Turbine is that single-stage is decided rotating speed mixed-flow Reversible Pump-Turbine.

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