CN106650117A - Method for design and model selection of low-pressure last stage blade of double back-pressure turboset - Google Patents
Method for design and model selection of low-pressure last stage blade of double back-pressure turboset Download PDFInfo
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Abstract
The invention discloses a method for design and model selection of low-pressure last stage blades of a double back-pressure turboset. By presetting thermodynamic design operating points of a turbine, a high-pressure side exhaust pressure Pb1 and a low-pressure side exhaust pressure Pb2 are determined, the exhaust volume flow Gv1 of a low-pressure cylinder on the low-pressure side and the exhaust volume flow Gv2 of the low-pressure cylinder on the high-pressure side are calculated, and finally according to the Gv1 and Gv2, the specification of a low-pressure side low-pressure last stage blade and the specification of a high-pressure side low-pressure last stage blade are selected respectively. Compared with an existing technology, the method has the advantages that the model selection method for configuring last stage blades with different lengths for two low-pressure cylinders with different back pressure is provided, so that under designed operating condition points, the residual velocity loss of the last stage blades on the two sides of the turbine is both minimum.
Description
Technical field
The present invention relates to the method for Steam Turbine in Fire Power Plant low pressure (LP) cylinder exhaust stage blade height type selecting, more particularly to one
Plant the design selection method of double back pressure turbine group low-pressure last stage blades.
Background technology
At present China 600MW and the exhaust turbine group of ratings above four adopt double pressure condenser mostly, but traditional
Therrmodynamic system design and the through-flow design of low pressure (LP) cylinder on still using being designed by the way of single back pressure unit, i.e., two difference steam discharges
The low pressure (LP) cylinder of pressure is divided equally according to flow, the principle with average exhaust steam pressure as back pressure is designed type selecting to exhaust stage blade.
Such as the average exhaust steam pressure 4.9kP low-pressure sides of Datang Nanjing Power Plant, high and low side exhaust pressure be respectively 5.4kP low-pressure sides and
4.4kP low-pressure sides, and in low-pressure last stage blade type selecting, be still designed according to average back pressure 4.9kP low-pressure side, and this is pressed
Power is variant with high and low pressure side steam turbine exhaust pressure.
The reasonable selection of low pressure (LP) cylinder exhaust stage blade is exactly to select steam discharge leaving loss most according to low pressure (LP) cylinder steam discharge volume flow
Little length of blade.And same low pressure (LP) cylinder steam discharge mass flow is under different exhaust steam pressures, the volume flow of low pressure (LP) cylinder steam discharge
Amount differs greatly, therefore traditional design method has obvious defect：Due to the actual exhaust steam pressure of two low pressure (LP) cylinders be different from it is flat
Exhaust steam pressure, causes the actual final stage leaving loss of two low pressure (LP) cylinders not in smallest point so that thermal loss of steam turbine rate ratio sets
Evaluation is higher.
The content of the invention
It is an object of the invention to overcome the deficiencies in the prior art, there is provided a kind of pair of back pressure turbine group low-pressure final stage leaf
The design selection method of piece.
The design selection method of a kind of pair of back pressure turbine group low-pressure last stage blade, it is characterised in that step is as follows：
Step one, default steam turbine thermal-design operating point, with determining the operating point for design according to average calculation of backpressure method
Tubine low pressure (LP) cylinder final stage exhaust steam flow G, low pressure (LP) cylinder initial steam pressure P0, steam admission enthalpy value H0, the average exhaust steam pressure P of low pressure (LP) cylinderb,
Circulating water flow W and circulating water temperature tw1；
Step 2, the parameter calculating determination high-pressure side exhaust steam pressure P obtained according to step oneb1With low-pressure side exhaust steam pressure
Pb2；
Step 3, respectively calculating low-pressure side low pressure (LP) cylinder delivery space flow Gv1With high-pressure side low pressure (LP) cylinder delivery space flow
Gv2；
Step 4, according to Gv1And Gv2The rule of low-pressure side low-pressure last stage blade and high-pressure side low-pressure last stage blade are selected respectively
Lattice.
As further improvement of these options, P in the step 2b1And Pb2Acquisition methods are as follows：
(1) the total heat exchange amount Q=G (h'-h of condenser is calculated0), wherein h' be exhaust enthalpy, h0For condensate enthalpy；
(2) recirculated water temperature rise △ t=Q/ (WC are calculatedv), wherein W be circulating water flow, CvFor recirculated water specific heat capacity；
(3) condenser gross area A is preset；
(4) low-pressure side condenser coefficient of heat transfer K is determined respectively according to HEI standards1, high-pressure side condenser coefficient of heat transfer K2；
(5) low-pressure side condenser pressure P is calculatedb1With high-pressure side condenser pressure Pb2：
For low-pressure side condenser
UtilizeCalculate low pressure side difference δ t1, wherein A1=A/2, △ t1=△ t/2；
Low-pressure side steam discharge saturation temperature ts1=tw1+△t1+δt1；
Low-pressure side condenser pressure P is obtained according to IF-97 vapor formulab1；
High-pressure side condenser pressure P is calculated in the same mannerb2With high-pressure side exhaust temperature ts2；
(6) determine average exhaust steam pressure, average exhaust temperature t is tried to achieve by IF-97 vapor formulas=(ts1+ts2)/2
Corresponding saturation pressure Pb'；
(7) if Pb'>Pb, then condenser area setting value A, and repeat step 3 are increased) and -7)；Otherwise reduce condenser area
Setting value A, and repeat step 3) -7)；Until Pb'=Pb, you can determine two back pressure of condenser Pb1、Pb2。
As further improvement of these options, G in the step 3v1And Gv2Preparation method it is as follows：
Calculate low-pressure side low pressure (LP) cylinder steam discharge volume flow：
By low pressure (LP) cylinder initial steam pressure P0, steam admission enthalpy value H0, obtained into vapour entropy S according to IF-97 vapor formula0,
Because low pressure (LP) cylinder exhaust steam pressure is less with low-pressure side condenser pressure difference, this case is equal to by low pressure (LP) cylinder exhaust steam pressure
Condenser pressure considers, by low-pressure side condenser pressure Pb1, enter vapour entropy S0, constant entropy steam discharge is obtained according to IF-97 vapor formula
Enthalpy Hsb1
The actual exhaust enthalpy of low-pressure side low pressure (LP) cylinder：Hb1=H0-(H0-Hsb1) × η, wherein η are low pressure (LP) cylinder design efficiency,
Because low pressure (LP) cylinder exhaust steam pressure is less with low-pressure side condenser pressure difference, this case is equal to by low pressure (LP) cylinder exhaust steam pressure
Condenser pressure considers, by low-pressure side condenser pressure Pb1, the actual exhaust enthalpy H of low pressure (LP) cylinderb1, obtained according to IF-97 vapor formula
Take steam discharge specific volume Vb1,
Calculate low-pressure side low pressure (LP) cylinder steam discharge volume flow：Gv1=G × Vb1/ 2,
By calculating high-pressure side low pressure (LP) cylinder steam discharge volume flow with calculating low-pressure side low pressure (LP) cylinder steam discharge volume flow same method
Amount Gv2。
Used as further improvement of these options, exhaust stage blade model is minimum in blade discharge loss curve to be clicked
Take.
As further improvement of these options, for 660MW unit initial values are set to 30000 ㎡, for 1000MW
Unit initial value is set to 50000 ㎡.
The present invention has compared to existing technology advantages below：Present invention is generally directed to double back pressure turbines, overcome existing skill
The deficiency of art method, there is provided a kind of new, more the design selection method of energy-conservation, i.e., the low pressure (LP) cylinder of two different back pressures is configured not
With the selection method of length exhaust stage blade, steam turbine will be caused under operating point for design, both sides exhaust stage blades leaving loss is most
It is little；It is determined that after steam turbine double pressure condenser design pressure, being damaged according to Steam Turbine Thermal Property, each model exhaust stage blade leaving velocity
The critical datas such as characteristic are lost, the different final blade length of two low pressure (LP) cylinders is determined, under making steam turbine thermal-design operating point, two
Individual low pressure (LP) cylinder final stage leaving loss is minimum.
Description of the drawings
Fig. 1 is the implementing procedure figure of the inventive method.
Fig. 2 is certain exhaust stage blade steam discharge loss curve legend.
Specific embodiment
Embodiments of the invention are elaborated below, the present embodiment is carried out under premised on technical solution of the present invention
Implement, give detailed embodiment and specific operating process, but protection scope of the present invention is not limited to following enforcements
Example.
The design selection method of a kind of pair of back pressure turbine group low-pressure last stage blade, implementing procedure figure is as shown in Figure 1.Its
In comprise the steps：
1st, steam turbine thermal-design operating point is determined.
Steam turbine thermal-design operating point is generally 100% rated load (base lotus unit), or with 75% rated load (waist
Lotus unit) it is operating point for design, on this basis, it is optimized design.After determining operating point for design, put down according to traditional first
Calculation of backpressure method calculates a tentative programme, and operating point for design tubine low pressure (LP) cylinder is obtained according to this tentative programme
Final stage exhaust steam flow G (kg/s), low pressure (LP) cylinder initial steam pressure P0, steam admission enthalpy value H0, the average exhaust steam pressure P of low pressure (LP) cylinderb.And according to this
Project actual environment condition obtains circulating water flow W, temperature tw1Deng Condenser Design boundary condition, (quantity of circulating water typically takes low pressure
50～70 times of circulating ratios of cylinder displacement).
For double back pressure turbines, two low pressure (LP) cylinders enter vapour and exhaust steam flow using the principle divided equally, two low pressure (LP) cylinder rows
Steam flow amount is G/2.
2nd, high and low pressure side exhaust steam pressure is determined.
Condenser heat exchange amount is mainly latent heat of phase change, and the different exchange heats of back pressure affect little.Therefore Condenser Design
The principle divided equally using both sides thermic load is carried out.
According to HEI standards, using both sides thermic load is identical, condenser area identical principle, calculates and determine high and low pressure side
Condenser Design pressure Pb1、Pb2.Because low pressure (LP) cylinder exhaust steam pressure is less with condenser pressure difference, low pressure (LP) cylinder steam discharge is pressed in this case
Pressure considers equal to condenser pressure.
Idiographic flow is as follows：
1) the total heat exchange amount Q=G (h'-h of condenser0), wherein h', h0Respectively exhaust enthalpy, condensate enthalpy；
2) according to recirculated water water yield W, heat exchange amount Q, recirculated water temperature rise △ t are determined：△ t=Q/ (WCv), wherein CvFor circulation
Water specific heat capacity.
3) the condenser gross area is set as A, and (660MW units initial value can be set to 30000 ㎡, 1000MW unit initial values
50000 ㎡ can be set to)；
4) low-pressure side condenser coefficient of heat transfer K is determined respectively according to HEI standards1, high-pressure side condenser coefficient of heat transfer K2；
5) for low-pressure side condenser：
Wherein A1=A/2, △ t1=△ t/2, can try to achieve low pressure side difference δ t1；
Low-pressure side steam discharge saturation temperature ts1=tw1+△t1+δt1；
Low-pressure side condenser pressure P can be drawn according to IF-97 vapor formulab1；
For high-pressure side condenser, high-pressure side exhaust temperature t can be obtained in the same manners2With high pressure condenser pressure Pb2。
6) average exhaust steam pressure determines：Average exhaust temperature t is tried to achieve by IF-97 vapor formulas=(ts1+ts2)/2 pair
The saturation pressure P for answeringb'。
If 7) Pb'>Pb, increase condenser area setting value A, and repeat step 3) and -7)；Otherwise reduce condenser area to set
Definite value A, and repeat step 3) -7)；Until Pb'=Pb, you can determine two back pressure of condenser Pb1、Pb2。
3rd, low pressure (LP) cylinder steam discharge volume flow
Two low pressure (LP) cylinder steam inlet conditions are identical, initial steam pressure P0, steam admission enthalpy value H0, low pressure (LP) cylinder design efficiency is η.
Low-pressure side low pressure (LP) cylinder steam discharge volume flow calculates method：
By low pressure (LP) cylinder initial steam pressure P0, steam admission enthalpy value H0, drawn into vapour entropy S according to IF-97 vapor formula0
By low-pressure side condenser pressure Pb1(i.e. low pressure (LP) cylinder exhaust steam pressure), enters vapour entropy S0, obtained according to IF-97 vapor formula
Go out constant entropy exhaust enthalpy Hsb1
The actual exhaust enthalpy of low-pressure side low pressure (LP) cylinder：Hb1=H0-(H0-Hsb1)×η
By low-pressure side condenser pressure Pb1(i.e. low pressure (LP) cylinder exhaust steam pressure), exhaust enthalpy Hb1, according to IF-97 vapor formula
Draw steam discharge specific volume Vb1
Can obtain, low-pressure side low pressure (LP) cylinder steam discharge volume flow：Gv1=G × Vb1/2
High-pressure side low pressure (LP) cylinder steam discharge volume flow G can be tried to achieve in the same mannerv2。
4th, according to all size low pressure (LP) cylinder exhaust stage blade performance data, different steam discharge volume flows select different final stages
Blade specification so that two low pressure (LP) cylinder design points are in steam discharge loss reduction value annex.See that accompanying drawing 2 selects respectively A, high-pressure side
Low pressure (LP) cylinder steam discharge volume flow Gv1、Gv2When, exhaust stage blade specification of the low pressure (LP) cylinder steam discharge leaving loss all near minimum of a value.
These are only presently preferred embodiments of the present invention, not to limit the present invention, all spirit in the present invention and
Any modification, equivalent and improvement for being made within principle etc., should be included within the scope of the present invention.
Claims (5)
1. the design selection method of a kind of pair of back pressure turbine group low-pressure last stage blade, it is characterised in that step is as follows：
Step one, default steam turbine thermal-design operating point, with determining vapour under the operating point for design according to average calculation of backpressure method
Turbine low pressure (LP) cylinder final stage exhaust steam flow G, low pressure (LP) cylinder initial steam pressure P0, steam admission enthalpy value H0, the average exhaust steam pressure P of low pressure (LP) cylinderb, circulation
Discharge W and circulating water temperature tw1；
Step 2, the parameter calculating determination high-pressure side exhaust steam pressure P obtained according to step oneb1With low-pressure side exhaust steam pressure Pb2；
Step 3, respectively calculating low-pressure side low pressure (LP) cylinder delivery space flow Gv1With high-pressure side low pressure (LP) cylinder delivery space flow Gv2；
Step 4, according to Gv1And Gv2The specification of low-pressure side low-pressure last stage blade and high-pressure side low-pressure last stage blade is selected respectively.
2. the as claimed in claim 1 design selection method of a kind of pair of back pressure turbine group low-pressure last stage blade, it is characterised in that：
P in the step 2b1And Pb2Acquisition methods are as follows：
(1) the total heat exchange amount Q=G (h'-h of condenser is calculated0), wherein h' be exhaust enthalpy, h0For condensate enthalpy；
(2) recirculated water temperature rise △ t=Q/ (WC are calculatedv), wherein W be circulating water flow, CvFor recirculated water specific heat capacity；
(3) condenser gross area A is preset；
(4) low-pressure side condenser coefficient of heat transfer K is determined respectively according to HEI standards1, high-pressure side condenser coefficient of heat transfer K2；
(5) low-pressure side condenser pressure P is calculatedb1With high-pressure side condenser pressure Pb2：
For low-pressure side condenser
UtilizeCalculate low pressure side difference δ t1, wherein A1=A/2, △ t1=△ t/2；
Low-pressure side steam discharge saturation temperature ts1=tw1+△t1+δt1；
Low-pressure side condenser pressure P is obtained according to IF-97 vapor formulab1；
High-pressure side condenser pressure P is calculated in the same mannerb2With high-pressure side exhaust temperature ts2；
(6) determine average exhaust steam pressure, average exhaust temperature is tried to achieve by IF-97 vapor formula
ts=(ts1+ts2The corresponding saturation pressure P ' in)/2b；
(7) if P 'b>Pb, then condenser area setting value A, and repeat step 3 are increased) and -7)；Otherwise reduce the setting of condenser area
Value A, and repeat step 3) -7)；Until P 'b=Pb, you can determine two back pressure of condenser Pb1、Pb2。
3. the as claimed in claim 1 design selection method of a kind of pair of back pressure turbine group low-pressure last stage blade, it is characterised in that
G in the step 3v1And Gv2Preparation method it is as follows：
Calculate low-pressure side low pressure (LP) cylinder steam discharge volume flow：
By low pressure (LP) cylinder initial steam pressure P0, steam admission enthalpy value H0, obtained into vapour entropy S according to IF-97 vapor formula0,
By low-pressure side condenser pressure Pb1, enter vapour entropy S0, constant entropy exhaust enthalpy H is obtained according to IF-97 vapor formulasb1
The actual exhaust enthalpy of low-pressure side low pressure (LP) cylinder：Hb1=H0-(H0-Hsb1) × η, wherein η are low pressure (LP) cylinder design efficiency,
By low-pressure side condenser pressure Pb1, the actual exhaust enthalpy H of low pressure (LP) cylinderb1, steam discharge specific volume is obtained according to IF-97 vapor formula
Vb1,
Calculate low-pressure side low pressure (LP) cylinder steam discharge volume flow：Gv1=G × Vb1/ 2,
By calculating high-pressure side low pressure (LP) cylinder steam discharge volume flow G with calculating low-pressure side low pressure (LP) cylinder steam discharge volume flow same methodv2。
4. the as claimed in claim 1 design selection method of a kind of pair of back pressure turbine group low-pressure last stage blade, it is characterised in that
Exhaust stage blade model minimal point in blade discharge loss curve is chosen.
5. the as claimed in claim 1 design selection method of a kind of pair of back pressure turbine group low-pressure last stage blade, it is characterised in that
For 660MW unit initial values are set to 30000 ㎡, for 1000MW unit initial values are set to 50000 ㎡.
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| CN108663216A (en) * | 2018-06-04 | 2018-10-16 | 西安热工研究院有限公司 | A kind of direct measuring method of turbine low pressure cylinder efficiency |
| CN109241573A (en) * | 2018-08-09 | 2019-01-18 | 国电南京电力试验研究有限公司 | A kind of last stage vane of steam turbine selection method |
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