CN102967464A - Method for evaluating performances of condensing steam turbine after high back pressure improvement - Google Patents

Method for evaluating performances of condensing steam turbine after high back pressure improvement Download PDF

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CN102967464A
CN102967464A CN2012105260538A CN201210526053A CN102967464A CN 102967464 A CN102967464 A CN 102967464A CN 2012105260538 A CN2012105260538 A CN 2012105260538A CN 201210526053 A CN201210526053 A CN 201210526053A CN 102967464 A CN102967464 A CN 102967464A
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steam
pressure
unit
enthalpy
high back
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CN102967464B (en
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王学栋
郑威
王学同
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State Grid Corp of China SGCC
Electric Power Research Institute of State Grid Shandong Electric Power Co Ltd
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State Grid Corp of China SGCC
Electric Power Research Institute of State Grid Shandong Electric Power Co Ltd
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Abstract

The invention discloses a method for evaluating performances of a condensing steam turbine after high back pressure improvement. The method comprises the following steps: distributing sufficient pressure, temperature, flow and electric power test points on a thermodynamic system of a turbine unit; stopping heating steam extraction on a low pressure cylinder gap bridge pipe; calculating the main steam flow, the cold reheat steam flow and the reheat steam flow; calculating the low pressure cylinder efficiency of a unit; taking a high back pressure heat supply unit as a pure condensing unit running under a high back pressure working condition, calculating the heat loss efficiency of the unit, and performing the second-type correction on the heat rate; and comparing the heat rate and the lower pressure cylinder efficiency with design values of a manufacture plant, and evaluating the lower pressure cylinder improvement technology and the unit improvement effect. The method disclosed by the invention is easy and feasible.

Description

The improved method of evaluating performance of condensing turbine high back pressure
Technical field
The present invention relates to a kind of method of evaluating performance, relate in particular to the improved method of evaluating performance of a kind of condensing turbine high back pressure.
Background technology
After the present invention relates to a kind of condensing turbine high back pressure heat supply transformation, performance test and the evaluation method of the operation of high back pressure operating mode.The high back pressure circulating water heating is that the pressure of steam condenser of steam turbine set is improved, and namely reduces the vacuum tightness of condenser, improves coolant water temperature, makes condenser become the heat exchangers for district heating of heating system, and chilled water is directly as heat supply network recirculated water, externally heat supply.The high back pressure circulating water heating takes full advantage of the vaporization latent heat recirculated water of condensing turbine steam discharge, and cold source energy is reduced to 0, thereby improves the unit thermal efficiency of cycle.
High back pressure circulating water heating Steam Turbine is the reworked unit that in recent years occurs for adapting to the northern heating heat supply, is mostly formed by the transformation of pure condensate Steam Turbine, and it is in recent years thing that large capacity reheat steam turbine group is carried out the transformation of high back pressure circulating water heating.Yantai power plant carried out the high back pressure heat supply of pure condensate 50MW unit and transformed in 2003, having carried out the high back pressure heat supply at the 150MW unit first in 2009 transforms, by the low pressure (LP) cylinder flow passage component is carried out the high back pressure transformation, realize the heat supply of unit high back pressure, for useful exploration has been carried out in the high back pressure circulating water heating transformation of UHV (ultra-high voltage) 135-150MW grade Steam Turbine.Ten li spring power plant of 2011 time electricity have carried out " two back pressure birotors exchange " and have transformed at the 140MW unit, turbine low pressure cylinder adopts two back pressure birotors to exchange renovation technique, it is the low pressure rotor that uses rotor and stator blade progression relatively to reduce during the heating, the low pressure rotor that non-heating period uses former design to be equipped with, the operation of Heating Period condenser high back pressure, non-heating period hangs down back pressure operation.
Large capacity reheat steam turbine group high back pressure transformation is thing in recent years, be in order to satisfy the needs of the thermal load that day by day increases at present, with regard to above two kinds of renovation techniques, modification scheme is also not exclusively ripe, occur some problems after the transformation, affected the unit safety economical operation.But because the machine unit in winter moves under the high back pressure state, there is not cold source energy, according to present Steam Turbine Performance test method and computing method, the high back pressure heat supply steam turbine is considered as the heat supply unit, the whole heating networks of the heat that recirculated water is taken away, unit has not had cold source energy, therefore the generatine set heat efficiency that calculates is relatively high, steam turbine just end condition and therrmodynamic system deviation is little to the correction of test findings, so the problem that turbine low pressure cylinder renovation technique, reforming part exist can not get exposing.Exchange renovation technique such as the two back pressure birotors of the ten li 140MW of spring power plant units, unit heating high back pressure in season is for the thermal condition operation, under 3VWO operating mode, VWO operating mode, sequence valve 110MW operating mode, 95MW operating mode, 80MW operating mode, the revised heat consumption rate of unit is 3670-3780kJ/kW.h, on average about 3710kJ/kW.h, the thermal efficiency is 96-98%.Just change with electric load, unit is in draw gas operating mode operation of high back pressure pure condensate operating mode or band heat supply, and unit heat consumption rate, the thermal efficiency change little.Under the 110MW condensing operating mode, unit test heat consumption rate 3724.188kJ/kW.h is 3723.806kJ/kW.h through the first revised heat consumption rate of end condition, and correction only is 0.382kJ/kW.h.
Take out solidifying or after the heat supply of pure condensate formula Steam Turbine high back pressure transforms, move under the thermal condition at high back pressure, with turbine discharge heating high temperature circulation water, realize external heat supply, economy is very high, generatine set heat efficiency reaches more than 94%, even unit is high, in, low pressure (LP) cylinder efficient does not reach design load, also only be to have reduced unit generation power, the thermoelectricity ratio of unit changes, but the thermal efficiency of unit is still higher, and since circulation water for heating flow and heating parameter alter a great deal, can't carry out one of unit test findings, two class corrections, test findings can't compare with design load under design conditions, therefore can't estimate the performance of condensing turbine high back pressure renovation technique and the rear flow passage component of transformation by the performance index evaluation method of common heat supply unit.
Summary of the invention
Purpose of the present invention is exactly in order to address the above problem, provide a kind of condensing turbine high back pressure improved method of evaluating performance, it has the improved performance of the steam turbine high back pressure heat supply of evaluation, provides the advantage that the performance evaluation of rear turbine body is transformed in the high back pressure heat supply.
To achieve these goals, the present invention adopts following technical scheme:
The method of evaluating performance that a kind of condensing turbine high back pressure is transformed, concrete steps are:
Step 1: arrange some pressure, temperature, flow, electric power test point in the Steam Turbine therrmodynamic system;
Step 2: the heating on the low pressure (LP) cylinder cross under of stopping using is drawn gas;
Step 3: calculate main steam flow, cold reheated steam flow and reheated steam flow;
Step 4: calculate unit low pressure (LP) cylinder efficient;
Step 5: high back pressure heat supply unit is considered as the pure condensate unit that the high back pressure operating mode is moved, calculates the unit heat consumption rate, and the fair curve that obtains according to the pure condensate unit derivation that unit is considered as the operation of high back pressure operating mode carries out two class corrections to heat consumption rate;
Step 6: the design load of revised heat consumption rate, low pressure (LP) cylinder efficient and manufacturing firm is compared, think poorly of cylinder pressure renovation technique and Transformation of Unit effect.
The concrete steps of described step 3 are:
(3-1) measure main steam enthalpy i Ms, reheated steam enthalpy i Rh, the final enthalpy i that feeds water Fw, cold reheated steam enthalpy i Ch, desuperheating water of superheater enthalpy i Ss, reheater desuperheating water enthalpy i Rs, the #1 height adds admission enthalpy i N1, #1 HP heater drainage enthalpy i S1, the #2 height adds admission enthalpy i N2, #2 HP heater drainage enthalpy i S2, the #1 height adds into water enthalpy i 11, the #1 height adds water outlet enthalpy i 12, the #2 height adds into water enthalpy i 21, the #2 height adds water outlet enthalpy i 22, generated output power Pe;
(3-2) measure feedwater flow G Fw, the equivalent flow G that changes of boiler drum level B1, desuperheating water of superheater flow G Ss, reheater desuperheating water flow G Rs
(3-3) the #2 height is added steam flow amount G E1, the #1 height adds steam flow amount G E2Obtained by the heat Balance Calculation that the #2 height adds, the #1 height adds; The #2 height is added the steam flow amount by formula G E1=G Fw* (i 22-i 21)/(i N2-i S2) calculate; The #1 height is added the steam flow amount by formula G E2=[G Fw* (i 12-i 11)-G E1(i S2-i S1)]/(i N1-i S1) calculate;
(3-4) utilize formula G Ms=G Fw+ G Bl+ G SsCalculate main steam flow G Ms
(3-5) high pressure cylinder door bar and antero posterior axis gland steam leakage rate sum G GlCalculate according to makers' thermodynamic property;
(3-6) according to formula G Ch=G Ms-G Gl-G E1-G E2Calculate cold reheated steam flow G Ch
(3-7) according to formula G Rh=G Ch+ G RsCalculate reheated steam flow G Rh
The concrete grammar of described step 4 is:
(4-1) measure low pressure (LP) cylinder admission enthalpy i LO
(4-2) utilize the steam turbine energy budget method to calculate low pressure (LP) cylinder exhaust enthalpy i Ex
(4-3) the actual enthalpy drop H of steam in low pressure (LP) cylinder iBy formula H i=i LO-i ExCalculate;
(4-4) utilize low pressure (LP) cylinder steam inlet condition and the exhaust steam pressure calculation of steam measured to calculate the interior entropy enthalpy drop H of low pressure (LP) cylinder 0
(4-5) low pressure (LP) cylinder efficient is η=H i/ H 0
The concrete steps of described step 5 are:
(5-1) high back pressure heat supply unit is considered as the pure condensate unit that the high back pressure operating mode is moved, utilizes formula H t=((G Ms-G Ss) * (i Ms-i Fw)+G Ch* (i Rh-i Ch)+G Ss* (i Ms-i Ss)+G Rs* (i Rh-i Rs))/Pe calculating unit heat consumption rate;
(5-2) according to the impact of first end condition on high back pressure pure condensate unit performance, calculate main steam pressure, main steam temperature, reheated steam crushing, reheat steam temperature, low pressure (LP) cylinder exhaust steam pressure to the correction factor of heat consumption rate, electric power.
Main steam pressure P OCorrection factor calculate: other initial parameters, final argument and therrmodynamic system parameter are guarantee value.Given different first pressing can obtain the N group about the data of main steam pressure, electric power and heat consumption rate through Thermodynamic Calculation Program, is respectively:
P 01 Ne 1 HR 1 P 02 Ne 2 HR 2 . . . . . . . . . P 0 N Ne N HR N
Wherein one group is that main steam pressure is the parameter of guarantee value, is P 0g, Ne g, HR gWith a certain main steam pressure P OXThe corresponding power of the assembling unit is Ne X, the unit heat consumption rate is HR XCompare the variation delta P of main steam pressure with guaranteeing parameter 0=(P 0x-P 0g)/P 0g, the variation delta Ne=Ne of power x/ Ne gVariation delta HR=HR with hear rate x/ HR gMain steam pressure correction factor C 1, K 1The variation delta Ne=Ne of the power that calculates exactly x/ Ne gVariation delta HR=HR with hear rate x/ HR gWith power and the heat consumption rate deviation percent under the specified main vapour pressure;
Main steam temperature T OCorrection factor calculate: other initial parameters, final argument and therrmodynamic system parameter are guarantee value, and given different initial temperature can obtain the N group about the data of main steam temperature, electric power and heat consumption rate through Thermodynamic Calculation Program, are respectively:
T 01 Ne 1 HR 1 T 02 Ne 2 HR 2 . . . . . . . . . T 0 N Ne N HR N
Wherein one group is that main steam temperature is the parameter of guarantee value, is T Og, Ne g, HR gWith a certain main stripping temperature T OXThe corresponding power of the assembling unit is Ne x, the unit heat consumption rate is HR X, then compare the variation delta T of main steam temperature with guaranteeing parameter 0=(T OX-T Og)/T Og, the variation delta Ne=Ne of power x/ Ne gVariation delta HR=HR with hear rate x/ HR gMain steam temperature correction factor C 2, K 2The variation delta Ne=Ne of the power that calculates exactly x/ Ne gVariation delta HR=HR with hear rate x/ HR gWith power and the heat consumption rate deviation percent under the specified main stripping temperature;
Reheated steam crushing DP RhCorrection factor calculate: other initial parameters, final argument and therrmodynamic system parameter are guarantee value.Given different reheated steam pressure can obtain the N group about the data of reheated steam crushing, electric power and heat consumption rate through Thermodynamic Calculation Program, is respectively:
DP rh 1 Ne 1 HR 1 DP rh 2 Ne 2 HR 2 . . . . . . . . . DP rhN Ne N HR N
Wherein one group is that reheated steam pressure is the parameter of guarantee value, is DP Rhg, Ne g, HR gWith a certain reheated steam crushing DP RhXThe corresponding power of the assembling unit is Ne x, the unit heat consumption rate is HR X, then compare the variation delta DP of reheated steam crushing with guaranteeing parameter Rh=(DP RhX-DP Rhg)/DP Rhg, the variation delta Ne=Ne of power x/ Ne gVariation delta HR=HR with hear rate x/ HR gReheated steam pressure correcting coefficient C3, K3 are exactly the variation delta Ne=Ne of the above power that calculates x/ Ne gVariation delta HR=HR with hear rate x/ HR gWith power and the heat consumption rate deviation percent under the specified reheated steam crushing;
Reheat steam temperature T RhCorrection factor calculate: other initial parameters, final argument and therrmodynamic system parameter are guarantee value.Given different reheat steam temperature can obtain the N group about the data of reheat steam temperature, electric power and heat consumption rate through Thermodynamic Calculation Program, is respectively:
T rh 1 Ne 1 HR 1 T rh 2 Ne 2 HR 2 . . . . . . . . . T rhN Ne N HR N
Wherein one group is that reheat steam temperature is the parameter of guarantee value, is T Rhg, Ne g, HR gWith a certain reheat steam temperature T RhXThe corresponding power of the assembling unit is Ne x, the unit heat consumption rate is HR X, then compare the variation delta T of reheat steam temperature with guaranteeing parameter Rh=(T RhX-T Rhg)/T Rhg, the variation delta Ne=Ne of power x/ Ne gVariation delta HR=HR with hear rate x/ HR gReheat steam temperature correction factor C 4, K 4The variation delta Ne=Ne of the power that calculates exactly x/ Ne gVariation delta HR=HR with hear rate x/ HR gWith power and the heat consumption rate deviation percent under the specified reheat steam temperature;
Condenser exhaust steam pressure P ExCorrection factor calculate: other initial parameters, therrmodynamic system parameter are guarantee value.Given different condenser exhaust steam pressure can obtain the N group about the data of condenser exhaust steam pressure, electric power and heat consumption rate through Thermodynamic Calculation Program, is respectively:
P ex 1 Ne 1 HR 1 P ex 2 Ne 2 HR 2 . . . . . . . . . P exN Ne N HR N
Wherein one group is that the condenser exhaust steam pressure is the parameter of guarantee value, is P Exg, Ne g, HR gWith a certain condenser exhaust steam pressure P ExxThe corresponding power of the assembling unit is Ne x, the unit heat consumption rate is HR X, then compare the variation delta P of condenser exhaust steam pressure with guaranteeing parameter Ex=(P Exx-P Exg)/P Exg, the variation delta Ne=Ne of power x/ Ne gVariation delta HR=HR with hear rate x/ HR gCondenser exhaust steam pressure correction factor C 5, K 5The variation delta Ne=Ne of the power that calculates exactly x/ Ne gVariation delta HR=HR with hear rate x/ HR gWith power and the heat consumption rate deviation percent under the specified condenser exhaust steam pressure;
(5-3) revised heat consumption rate is H r=H t/ (C 1* C 2* C 3* C 4* C 5), revised electric power is P Er=P e/ (K 1* K 2* K 3* K 4* K 5); Wherein, C 1, C 2, C 3, C 4, C 5Respectively that main steam pressure, main steam temperature, reheated steam crushing, reheat steam temperature, low pressure (LP) cylinder exhaust steam pressure are to the correction factor of heat consumption rate; K 1, K 2, K 3, K 4, K 5Respectively that main steam pressure, main steam temperature, reheated steam crushing, reheat steam temperature, low pressure (LP) cylinder exhaust steam pressure are to the correction factor of electric power.
Beneficial effect of the present invention:
(1) high back pressure heat supply steam turbine group is considered as the condensing turbine group that the high back pressure operating mode is moved.The heating that stops unit during test draw gas (having the heating of external heat supply to draw gas such as unit), with the pure condensed steam unit of steam turbine as the operation of high back pressure operating mode, can use like this GB/T8117-2008 " steam turbine performance reception test rules " to come low pressure (LP) cylinder efficient and the heat consumption rate of measuring and calculation unit.
(2) according to the impact of first end condition on high back pressure operating mode operation pure condensate unit, calculate main steam pressure, main steam temperature, reheated steam crushing, reheat steam temperature, low pressure (LP) cylinder exhaust steam pressure to the correction factor of unit heat consumption rate and electric power.The first end condition fair curve that manufacturing plant provides obtains according to heat supply unit pattern, and is little on the correction of unit heat consumption rate and thermal efficiency impact, can not embody first end condition deviation and therrmodynamic system deviation to the impact of equipment performance.As being considered as the condensing unit of high back pressure operating mode operation, the method for available condensing unit is derived and is revised the performance index of unit.With fair curve correction unit low pressure (LP) cylinder efficient and the heat consumption rate of the first end condition that calculates to high back pressure condensing unit performance impact, and the design load of correction result and manufacturing firm compared, think poorly of cylinder pressure renovation technique and Transformation of Unit effect.
(3) calculated high back pressure heat supply unit as the condensing unit, low pressure (LP) cylinder efficient and the unit heat consumption rate of the operation of high back pressure condensing operating mode, the unit heat consumption rate is carried out two class corrections, and low pressure (LP) cylinder efficient and unit heat consumption rate and design load compared, ignored the factors that low pressure (LP) cylinder efficient and unit heat consumption rate are affected by circulating water temperature and quantity of circulating water, the method simple possible.
Description of drawings
Fig. 1 is Steam Turbine therrmodynamic system measuring point arrangenent diagram of the present invention;
Fig. 2 (a) first pressing is on the fair curve of heat consumption rate and electric power impact;
Fig. 2 (b) initial temperature is on the fair curve of heat consumption rate and electric power impact;
Fig. 2 (c) reheat temperature is on the fair curve of heat consumption rate and electric power impact;
The fair curve on heat consumption rate and electric power impact is decreased in Fig. 2 (d) hot repressing;
Fig. 2 (e) back pressure is on the fair curve of heat consumption rate and electric power impact;
Fig. 3 is low pressure (LP) cylinder steam discharge loss fair curve.
Embodiment
The invention will be further described below in conjunction with accompanying drawing and embodiment.
Certain 140MW steam turbine is former to be the UHV (ultra-high voltage) unit of being produced by Shanghai Turbine Co., Ltd.For realizing the heat supply of unit high back pressure, the low pressure (LP) cylinder flow passage component is transformed, and heating season, low pressure (LP) cylinder adopts the high back pressure rotor that removes last two-stage dividing plate, movable vane.Pattern behind the Transformation of Unit: UHV (ultra-high voltage), resuperheat, twin-tub, a double flow, singly take out, condensing turbine; Model: N112/C112-13.24/0.24/535/535 type; The condenser exhaust steam pressure (drawing gas/condensation) of high back pressure operation: 43.6kPa; The unit heat consumption rate (drawing gas/condensation) of high back pressure operation: 3684.8/3776.6kJ/kW.h.
Carry out Steam Turbine Performance test according to GB/T8117-2008 " steam turbine performance reception test rules ", the layout of test measuring point is according to as shown in Figure 1.
Unit measuring system and measurement instrument: (1) electric power measurement: generator power is measured at 0.02 grade of qualified WT3000 power transducer of the outlet termination verification of generator.(2) flow measurement: condensing water flow adopts throat's pressure Long Nozzle of standard and 0.075 grade of 3051 differential pressure transmitter to measure, the condensing water flow nozzle is contained on the low horizontal pipeline that adds between outlet and the oxygen-eliminating device import of #4, and demarcates through the inspection center that qualification is arranged in advance.Superheater, reheater desuperheating water flow are measured with standard orifice plate; Sealing Water for Feedwater Pump inflow and circling water flow rate install water meter additional to be measured.(3) pressure survey: all pressure-measuring-points are with 0.1 grade of 3051 pressure transmitter measurement.(4) temperature survey: all temperature points industrial one-level E calibration armoured thermocouple that changes the outfit.
The IMP discrete data acquisition device that all the data Shi Lunbaijie companies produce, the adapted portable computer gathers, and collection period is 30 seconds.The test raw data that collects is carried out arithmetic mean by the metastable one continuous recording period of operating mode calculate, pressure-measuring-point carries out absolute altitude and atmospheric pressure correction.The measured value of the multiple measuring point of same parameters in the test is got its arithmetic mean.
List the test raw data under the 110MW operating mode after the transformation of unit high back pressure in the table 1, list the test corrected Calculation result under the 110MW operating mode after the transformation of unit high back pressure in the table 2.
110MW working condition tests raw data after the transformation of table 1 UHV (ultra-high voltage) 140MW unit high back pressure
Sequence number The measuring point title Unit The 110MW operating mode
1 Generator active power kW 110027
2 The main steam temperature first ℃ 534.492
3 Main steam temperature second ℃ 533.086
4 High row's vapor (steam) temperature first ℃ 322.196
5 High row's vapor (steam) temperature second ℃ 324.296
6 The reheat steam temperature first ℃ 532.461
7 Reheat steam temperature second ℃ 535.236
8 Middle row's vapor (steam) temperature first ℃ 295.905
9 Middle row's vapor (steam) temperature second ℃ 297.066
10 One section extraction temperature ℃ 394.539
11 Three sections extraction temperatures ℃ 461.946
12 The oxygen-eliminating device throttle (steam) temperature ℃ 319.674
13 Four sections extraction temperatures ℃ 171.147
14 Five sections extraction temperatures ℃ 295.596
15 Six sections extraction temperatures ℃ 242.897
16 The low throttle (steam) temperature that adds of #2 ℃ 203.179
17 Axle adds inflow temperature ℃ 81.460
18 The hot well water temperature ℃ 81.501
19 The low inflow temperature that adds of #2 ℃ 73.675
20 The low leaving water temperature that adds of #2 ℃ 88.415
21 #2 low plus hydrophobic temperature ℃ 92.303
22 The low inflow temperature that adds of #3 ℃ 88.461
23 The low leaving water temperature that adds of #3 ℃ 135.465
24 #3 low plus hydrophobic temperature ℃ 139.226
25 #4 low plus hydrophobic temperature ℃ 36.510
26 The low leaving water temperature that adds of #4 ℃ 135.853
27 Coolant-temperature gage under the oxygen-eliminating device ℃ 157.334
28 The #1 height adds inflow temperature ℃ 157.931
29 #1 HP heater drainage temperature ℃ 191.025
30 The #1 height adds leaving water temperature ℃ 217.494
31 #2 HP heater drainage temperature ℃ 236.930
32 The #2 height adds leaving water temperature ℃ 238.599
33 Recirculated water inflow temperature first ℃ 51.802
34 Recirculated water inflow temperature second ℃ 52.856
35 Recirculated water leaving water temperature first ℃ 77.556
36 Recirculated water leaving water temperature second ℃ 76.311
37 The main steam pressure first MPa 13.0915
38 Main steam pressure second MPa 13.1923
39 Pressure behind the governing stage MPa 9.0266
40 High row's vapor pressure first MPa 2.5052
41 High row's vapor pressure second MPa 2.5071
42 Reheated steam pressure first MPa 2.3418
43 Reheated steam pressure second MPa 2.3379
44 Middle row's vapor pressure first MPa 0.3464
45 Middle row's vapor pressure second MPa 0.3464
46 One section extraction pressure MPa 3.4037
47 The #2 height adds initial steam pressure MPa 3.2065
48 The #1 height adds initial steam pressure MPa 2.437
49 Three sections extraction pressures MPa 0.7489
50 The oxygen-eliminating device initial steam pressure MPa 0.655
51 Four sections extraction pressures MPa 0.5131
52 The low initial steam pressure that adds of #4 MPa 0.3225
53 Five sections extraction pressures MPa 0.3753
54 The low initial steam pressure that adds of #3 MPa 0.3748
55 Six sections extraction pressures MPa 0.102
56 The low initial steam pressure that adds of #2 kPa 79.84
57 Low pressure (LP) cylinder exhaust steam pressure one kPa 52.236
58 Low pressure (LP) cylinder exhaust steam pressure two kPa 52.492
59 Feed pressure MPa 15.0902
60 Pressure of desuperheating water of superheater MPa 15.0697
61 The reheater pressure of desuperheating water MPa 7.6046
62 Condensing water flow nozzle place pressure MPa 0.8187
63 Recirculated water intake pressure first MPa 0.3108
64 Recirculated water intake pressure second MPa 0.3137
65 Recirculated water discharge pressure first MPa 0.2997
66 Recirculated water discharge pressure second MPa 0.2997
67 Atmospheric pressure kPa 102.0
68 Main condensate flow differential pressure one kPa 47.659
69 Main condensate flow differential pressure two kPa 48.346
70 Desuperheating water of superheater flow differential pressure kPa 6.098
71 Reheater desuperheating water flow differential pressure kPa 33.228
72 The Sealing Water for Feedwater Pump water supply flow t/h 23.02
73 The Sealing Water for Feedwater Pump circling water flow rate t/h 10.25
74 The circulation water for heating flow t/h 7070.609
75 Deaerator storage tank is water level just mm 2127.66
76 The whole water level of deaerator storage tank mm 2132.23
77 The heat exchangers for district heating discharge pressure MPa 1.6113
This test with condensing water flow as calculating benchmark, the thermal equilibrium and the mass balance that add with oxygen-eliminating device according to #1, #2 height calculate feedwater flow, then calculate main steam flow, reheated steam flow, high pressure cylinder exhaust steam flow (cold reheated steam flow), as shown in table 2.
110MW working condition tests result after the transformation of table 2 UHV (ultra-high voltage) 140MW unit high back pressure
Sequence number Parameter Unit The 110MW operating mode
1 Generator power kW 110027
2 Main steam temperature ℃ 533.789
3 Main steam pressure MPa 13.1419
4 Main steam flow kg/h 381331.1
5 Reheat steam temperature ℃ 533.849
6 Reheated steam pressure MPa 2.340
7 The reheated steam flow kg/h 336383.2
8 High row's vapor (steam) temperature ℃ 323.246
9 High row's vapor pressure MPa 2.5062
10 High row's steam flow kg/h 310348.2
11 Middle row's vapor (steam) temperature ℃ 296.486
12 Middle row's vapor pressure MPa 0.3753
13 Back pressure of condenser kPa 52.364
14 Feed temperature ℃ 238.599
15 Feed pressure MPa 15.0902
Sequence number Parameter Unit The 110MW operating mode
16 Feedwater flow kg/h 369157.1
17 One section extraction pressure MPa 3.4037
18 One section extraction temperature ℃ 394.539
19 The #2 height is added the steam flow amount kg/h 16234.3
20 Two sections extraction pressures MPa 2.5062
21 Two sections extraction temperatures ℃ 323.246
22 The #1 height is added the steam flow amount kg/h 41250.7
23 Three sections extraction pressures MPa 0.7489
24 Three sections extraction temperatures ℃ 338.610
25 Oxygen-eliminating device admission flow kg/h 9961.8
26 The desuperheating water of superheater temperature ℃ 157.931
27 Pressure of desuperheating water of superheater MPa 15.0697
28 The desuperheating water of superheater flow kg/h 12174
29 Reheater desuperheating water temperature ℃ 157.633
30 The reheater pressure of desuperheating water MPa 7.6046
31 Reheater desuperheating water flow kg/h 26035
32 Condensing water flow kg/h 328547
33 The circulation water for heating flow t/h 7070.609
34 The recirculated water discharge pressure MPa 0.2997
35 The recirculated water leaving water temperature ℃ 76.934
36 The recirculated water intake pressure MPa 0.3123
37 The recirculated water inflow temperature ℃ 52.329
38 The high pressure cylinder actual enthalpy drop kJ/kg 359.356
39 The high pressure cylinder isentropic enthalpy drop, ideal enthalpy drop kJ/kg 469.740
40 High pressure cylinder efficient % 76.501
41 The intermediate pressure cylinder actual enthalpy drop kJ/kg 477.859
42 The intermediate pressure cylinder isentropic enthalpy drop, ideal enthalpy drop kJ/kg 551.762
43 Intermediate pressure cylinder efficient % 86.606
44 Low pressure (LP) cylinder exhaust enthalpy UEEP kJ/kg 2704.07
45 The low pressure (LP) cylinder actual enthalpy drop kJ/kg 356.552
46 The low pressure (LP) cylinder isentropic enthalpy drop, ideal enthalpy drop kJ/kg 410.547
47 Low pressure (LP) cylinder UEEP efficient ％ 86.848
48 Low pressure (LP) cylinder ELEP efficient ％ 87.15
Sequence number Parameter Unit The 110MW operating mode
49 The test heat consumption rate kJ/kW.h 10343.48
50 The test specific steam consumption kg/kW.h 3.4658
51 Main steam pressure is to the heat consumption rate correction factor ------ 1.000729
52 Main steam pressure is to the electric power correction factor ------ 0.991237
53 Main steam temperature is to the heat consumption rate correction factor ------ 1.000477
54 Main steam temperature is to the electric power correction factor ------ 1.000068
55 Reheat steam temperature is to the heat consumption rate correction factor ------ 1.000373
56 Reheat steam temperature is to the electric power correction factor ------ 0.998842
57 The reheated steam crushing ％ 6.632
58 The reheated steam crushing is to the heat consumption rate correction factor ------ 0.997557
59 The reheated steam crushing is to the electric power correction factor ------ 1.007911
60 Exhaust steam pressure is to the heat consumption rate correction factor ------ 1.013396
61 Exhaust steam pressure is to the electric power correction factor ------ 0.986697
62 To the total correction factor of heat consumption rate ------ 1.012518
63 To the total correction factor of electric power ------ 0.984713
64 The revised electric power of two classes kW 111735.1
65 The revised heat consumption rate of two classes kJ/kW.h 10215.61
66 Main steam flow after revising kg/h 383889.6
67 The revised specific steam consumption of two classes kg/kW.h 3.4357
68 Generatine set heat efficiency ％ 35.240
This UHV (ultra-high voltage) 140MW unit high back pressure Heating State is considered as the pure condensate unit of high back pressure operating mode operation, according to manufacturing plant's design calculation, calculate under the high back pressure 112MW condensing operating mode, the unit design heat consumption rate is 9776.61kJ/kW.h, and design low pressure (LP) cylinder efficient is 91.34%; And in the heating power calculated description unit being considered as high back pressure heat supply unit, the design heat consumption rate that provides under the 112MW operating mode is 3776.6kJ/kW.h.
The improved performance test of unit high back pressure, as high back pressure heat supply unit, under the high back pressure condensing 110MW operating mode, the test heat consumption rate is 3724.188kJ/kW.h with unit, and heat consumption rate is 3723.806kJ/kW.h after revising, and generatine set heat efficiency is 96.675%; Because circulating water flow is higher than design load, revised heat consumption rate is lower than design load under the unit operating condition of test; Just end condition off-design value is very little to the correction of test findings, the fair curve that utilizes manufacturing plant to provide, obtaining five total correction factors to unit test heat consumption rate of main steam pressure, main steam temperature, reheat steam temperature, reheated steam crushing, low pressure (LP) cylinder exhaust steam pressure is 1.000103.And unit is considered as the pure condensed steam unit that the high back pressure operating mode is moved, the revised heat consumption rate of unit is 10215.61kJ/kW.h, low pressure (LP) cylinder UEEP efficient is 86.848%, heat consumption rate and the low pressure (LP) cylinder efficient of the operation of unit high back pressure condensing operating mode all do not reach design load, and because low pressure (LP) cylinder exhaust steam pressure off-design value is larger, just end condition is large to the correction of unit test findings, the first end condition of deriving according to the pure condensate unit that unit is considered as high back pressure operating mode operation calculates main steam pressure to the fair curve of unit performance impact, main steam temperature, reheat steam temperature, the reheated steam crushing, five total correction factors to unit test heat consumption rate of low pressure (LP) cylinder exhaust steam pressure are 1.012518.
Under the more same operating mode, the improved performance test results of Steam Turbine high back pressure, as the condensing unit of heat supply unit or high back pressure operation, the conclusion (of pressure testing) that draws is fully opposite.As high back pressure heat supply unit, revised heat consumption rate is lower than design load under the unit operating condition of test, and first end condition is little to the correction of unit heat consumption rate; As the condensing unit of high back pressure operation, revised heat consumption rate and low pressure (LP) cylinder efficient all do not reach design load under the unit operating condition of test, and first end condition is large to the correction of unit heat consumption rate.Basic reason is the improved steam turbine of high back pressure, and externally circulation water for heating has been taken away a large amount of heats, and this part heat and pipe network thermal load, circulating water temperature and circulating water flow are in close relations, and is subjected at the beginning of the unit impact of end condition little.Therefore for the improved steam turbine of high back pressure heat supply, conventional heat supply unit Calculation Methods for Performance is not suitable for the improved low pressure (LP) cylinder performance of determination and analysis steam turbine high back pressure and unit heat consumption rate.And the pure condensed steam unit that use that the present invention recommends high back pressure heat supply unit is considered as moved under the high back pressure operating mode calculates turbine low pressure cylinder efficient and unit heat consumption rate, analyzes improved low pressure (LP) cylinder performance, unit performance and renovation technique itself.
Fig. 2 (a) first pressing is on the fair curve of heat consumption rate and electric power impact;
Fig. 2 (b) initial temperature is on the fair curve of heat consumption rate and electric power impact;
Fig. 2 (c) reheat temperature is on the fair curve of heat consumption rate and electric power impact;
The fair curve on heat consumption rate and electric power impact is decreased in Fig. 2 (d) hot repressing;
Fig. 2 (e) back pressure is on the fair curve of heat consumption rate and electric power impact;
Be illustrated in figure 3 as low pressure (LP) cylinder steam discharge loss fair curve.
Although above-mentionedly by reference to the accompanying drawings the specific embodiment of the present invention is described; but be not limiting the scope of the invention; one of ordinary skill in the art should be understood that; on the basis of technical scheme of the present invention, those skilled in the art do not need to pay various modifications that creative work can make or distortion still in protection scope of the present invention.

Claims (4)

1. the method for evaluating performance transformed of a condensing turbine high back pressure is characterized in that concrete steps are:
Step 1: arrange some pressure, temperature, flow, electric power test point in the Steam Turbine therrmodynamic system;
Step 2: the heating on the low pressure (LP) cylinder cross under of stopping using is drawn gas;
Step 3: calculate main steam flow, cold reheated steam flow and reheated steam flow;
Step 4: calculate unit low pressure (LP) cylinder efficient;
Step 5: high back pressure heat supply unit is considered as the pure condensate unit that the high back pressure operating mode is moved, calculates the unit heat consumption rate, and the fair curve that obtains according to the pure condensate unit derivation that unit is considered as the operation of high back pressure operating mode carries out two class corrections to heat consumption rate;
Step 6: the design load of revised heat consumption rate, low pressure (LP) cylinder efficient and manufacturing firm is compared, think poorly of cylinder pressure renovation technique and Transformation of Unit effect.
2. the method for evaluating performance transformed of a kind of condensing turbine high back pressure as claimed in claim 1 is characterized in that the concrete grammar of described step 3 is:
(3-1) measure main steam enthalpy i Ms, reheated steam enthalpy i Rh, the final enthalpy i that feeds water Fw, cold reheated steam enthalpy i Ch, desuperheating water of superheater enthalpy i Ss, reheater desuperheating water enthalpy i Rs, the #1 height adds admission enthalpy i N1, #1 HP heater drainage enthalpy i S1, the #2 height adds admission enthalpy i N2, #2 HP heater drainage enthalpy i S2, the #1 height adds into water enthalpy i 11, the #1 height adds water outlet enthalpy i 12, the #2 height adds into water enthalpy i 21, the #2 height adds water outlet enthalpy i 22, generated output power Pe;
(3-2) measure feedwater flow G Fw, the equivalent flow G that changes of boiler drum level B1, desuperheating water of superheater flow G Ss, reheater desuperheating water flow G Rs
(3-3) the #2 height is added steam flow amount G E1, the #1 height adds steam flow amount G E2By the #2 height add, the #1 number high heat Balance Calculation that adds obtains; The #2 height is added the steam flow amount by formula G E1=G Fw* (i 22-i 21)/(i N2-i S2) calculate; The #1 height is added the steam flow amount by formula G E2=[G Fw* (i 12-i 11)-G E1(i S2-i S1)]/(i N1-i S1) calculate;
(3-4) utilize formula G Ms=G Fw+ G Bl+ G SsCalculate main steam flow G Ms
(3-5) high pressure cylinder door bar and antero posterior axis gland steam leakage rate sum G GlCalculate value according to makers' thermodynamic property;
(3-6) according to formula G Ch=G Ms-G G1-G E1-G E2Calculate cold reheated steam flow G Ch
(3-7) according to formula G Rh=G Ch+ G RsCalculate reheated steam flow G Rh
3. the method for evaluating performance transformed of a kind of condensing turbine high back pressure as claimed in claim 1 is characterized in that the concrete steps of described step 4 are:
(4-1) measure low pressure (LP) cylinder admission enthalpy i L0
(4-2) utilize the steam turbine energy budget method to calculate low pressure (LP) cylinder exhaust enthalpy i Ex
(4-3) the actual enthalpy drop H of steam in low pressure (LP) cylinder iBy formula H i=i LO-i ExCalculate;
(4-4) utilize low pressure (LP) cylinder steam inlet condition and the isentropic enthalpy drop, ideal enthalpy drop H of exhaust steam pressure calculation of steam in low pressure (LP) cylinder that measures 0
(4-5) low pressure (LP) cylinder efficient is η=H i/ H 0
4. the method for evaluating performance transformed of a kind of condensing turbine high back pressure as claimed in claim 1 is characterized in that the concrete steps of described step 5 are:
(5-1) unit is considered as the pure condensate unit that the high back pressure operating mode is moved, utilizes formula H t=((G Ms-G Ss) * (i Ms-i Fw)+G Ch* (i Rh-i Ch)+G Ss* (i Ms-i Ss)+G Rs* (i Rh-i Rs))/Pe calculating unit heat consumption rate;
(5-2) according to the impact on high back pressure pure condensate unit performance of initial parameter, final argument, calculate main steam pressure, main steam temperature, reheated steam crushing, reheat steam temperature, low pressure (LP) cylinder exhaust steam pressure to the correction factor of heat consumption rate, electric power;
(5-3) revised heat consumption rate is H r=H t/ (C 1* C 2* C 3* C 4* C 5), revised electric power is P Er==P e/ (K 1* K 2* K 3* K 4* K 5); Wherein, C 1, C 2, C 3, C 4, C 5Respectively that main steam pressure, main steam temperature, reheated steam crushing, reheat steam temperature, low pressure (LP) cylinder exhaust steam pressure are to the correction factor of heat consumption rate; K 1, K 2, K 3, K 4, K 5Respectively that main steam pressure, main steam temperature, reheated steam crushing, reheat steam temperature, low pressure (LP) cylinder exhaust steam pressure are to the correction factor of electric power.
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CN113049284A (en) * 2021-03-26 2021-06-29 西安西热节能技术有限公司 Low-pressure cylinder zero-output safety monitoring and evaluating method suitable for wet-cooling 300MW unit
CN113187568A (en) * 2021-05-28 2021-07-30 西安热工研究院有限公司 System and method for reversely improving power supply and heat supply capacity of high-backpressure heat supply unit
CN114943127A (en) * 2022-06-28 2022-08-26 西安热工研究院有限公司 Calculation method for correcting steam turbine sequence valve state to single valve state

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