CN114943127A - Calculation method for correcting steam turbine sequence valve state to single valve state - Google Patents
Calculation method for correcting steam turbine sequence valve state to single valve state Download PDFInfo
- Publication number
- CN114943127A CN114943127A CN202210742265.3A CN202210742265A CN114943127A CN 114943127 A CN114943127 A CN 114943127A CN 202210742265 A CN202210742265 A CN 202210742265A CN 114943127 A CN114943127 A CN 114943127A
- Authority
- CN
- China
- Prior art keywords
- steam
- steam turbine
- overhaul
- pressure cylinder
- representing
- 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
Images
Classifications
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/10—Geometric CAD
- G06F30/17—Mechanical parametric or variational design
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D21/00—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/30—Application in turbines
- F05D2220/31—Application in turbines in steam turbines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2270/00—Control
- F05D2270/30—Control parameters, e.g. input parameters
- F05D2270/301—Pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2270/00—Control
- F05D2270/30—Control parameters, e.g. input parameters
- F05D2270/303—Temperature
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2111/00—Details relating to CAD techniques
- G06F2111/10—Numerical modelling
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/08—Thermal analysis or thermal optimisation
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/14—Force analysis or force optimisation, e.g. static or dynamic forces
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- Theoretical Computer Science (AREA)
- General Physics & Mathematics (AREA)
- General Engineering & Computer Science (AREA)
- Pure & Applied Mathematics (AREA)
- Mathematical Optimization (AREA)
- Computer Hardware Design (AREA)
- Evolutionary Computation (AREA)
- Mathematical Analysis (AREA)
- Computational Mathematics (AREA)
- Mechanical Engineering (AREA)
- Control Of Turbines (AREA)
Abstract
The invention discloses a calculation method for correcting the state of a sequence valve of a steam turbine to be in a single-valve state, which comprises the following steps: calculating the high-pressure cylinder efficiency and the regulation level to high-pressure cylinder steam exhaust expansion section cylinder efficiency of the steam turbine before overhaul under a set working condition, calculating the high-pressure cylinder efficiency and the regulation level to high-pressure cylinder steam exhaust expansion section cylinder efficiency of the steam turbine after overhaul under the set working condition, calculating the high-pressure cylinder efficiency lifting percentage point of the steam turbine before overhaul and the high-pressure cylinder efficiency lifting percentage point of steam turbine after the overhaul to the high-pressure cylinder steam exhaust expansion section cylinder efficiency after overhaul, calculating the single valve to sequence valve cylinder efficiency single lifting percentage point of the steam turbine, determining the absolute influence quantity of one percentage point of the high-pressure cylinder efficiency lifting of the steam turbine to the steam turbine heat consumption rate, calculating the heat consumption rate correction quantity of the steam turbine from the sequence valve state after overhaul to the single valve state, and calculating the heat consumption rate from the sequence valve state after overhaul to the single valve state. The invention can correct the heat rate of the steam turbine in the sequence valve state to the heat rate in the single valve state.
Description
Technical Field
The invention belongs to the technical field of power generation, and particularly relates to a calculation method for correcting a steam turbine sequence valve state to a single valve state.
Background
Because the operating states of the steam turbine before and after overhaul are limited by field conditions, the operating states of the steam turbine before and after overhaul are generally difficult to be unified to the same reference. In order to correct the operation states of the steam turbine before and after overhaul to the same standard, a first type correction method and a second type correction method are provided in the ASME PTC 2004 standard. The first kind of correction method mainly performs system correction, and the system correction usually includes correction items such as extraction steam pressure loss, heater end difference, enthalpy rise of a feed water pump, small machine steam inlet flow and the like. The second type of correction method generally includes correction items such as main steam pressure, main steam temperature, reheat steam temperature, reheater pressure loss, exhaust steam pressure, and the like. However, neither the first type correction method nor the second type correction method corrects the valve sequence or the valve overlap degree of the turbine operation.
The heat rate at which the turbine operates in the single valve regime is different from the heat rate at which the turbine operates in the sequential valve regime. Generally, the heat consumption rate of the steam turbine running in the same load sequence valve state is lower than that of the steam turbine running in the same load single valve state, and the economy is better. However, when performing performance tests before and after turbine overhaul, the problem that only a sequence valve can be operated after overhaul before overhaul or only a sequence valve can be operated after overhaul before overhaul is usually encountered.
Disclosure of Invention
The invention aims to provide a correcting method for correcting the state of a sequence valve of a steam turbine to a state of a single valve, which has strong applicability, is convenient and reliable.
The invention is realized by adopting the following technical scheme:
a calculation method for correcting the state of a sequence valve of a steam turbine to a single valve state comprises the following steps:
step 1: setting the steam turbine to operate under a single valve before overhaul, and operating the steam turbine under a sequence valve after overhaul for calculation;
step 2: measuring main steam pressure P of steam turbine under set working condition before overhaul ms Main steam temperature T ms Post-regulation stage steam pressure P tj Regulating the post-stage steam temperature T tj Exhaust pressure P of high-pressure cylinder gp And high pressure Cylinder exhaust temperature T gp ；
And step 3: calculating the high-pressure cylinder efficiency of the steam turbine under a set working condition before overhaul and the cylinder efficiency of the steam exhaust expansion section of the high-pressure cylinder of the regulating stage;
and 4, step 4: measuring main steam pressure P 'of turbine under set working condition after overhaul' ms Of main steam temperature T' ms Regulated post stage steam pressure P' tj Post-regulated steam temperature T' tj Exhaust pressure P 'of high pressure cylinder' gp And high-pressure cylinder exhaust temperature T' gp ；
And 5: calculating the high-pressure cylinder efficiency of the steam turbine under the set working condition after overhaul and the cylinder efficiency of the steam exhaust expansion section of the regulating stage to the high-pressure cylinder;
and 6: calculating the efficiency improvement percentage point of the high-pressure cylinder of the steam turbine before and after overhaul and the efficiency improvement percentage point of the steam of the regulating stage of the steam turbine before and after overhaul to the steam exhaust expansion section of the high-pressure cylinder;
and 7: calculating the single improvement percentage point of the efficiency from the single valve to the sequential valve cylinder of the steam turbine, and representing the single improvement percentage point by a symbol delta eta;
and 8: according to the type of the steam turbine, relevant documents are consulted to determine the absolute influence quantity of the efficiency improvement of the high-pressure cylinder of the steam turbine on the heat consumption rate of the steam turbine, wherein the absolute influence quantity is represented by a symbol h;
and step 9: calculating the heat consumption rate correction amount of the steam turbine from the sequence valve state after the overhaul to the single valve state, and taking the symbol delta HR v Represents;
step 10: and calculating the heat consumption rate from the state of the sequence valve after the overhaul to the state of the single valve.
The invention is further improved in that in the step 2, the units adopting the variables adopt the international system of units.
The further improvement of the invention is that in step 3, the high-pressure cylinder efficiency and the regulation level of the steam turbine to the high-pressure cylinder steam exhaust expansion section cylinder efficiency under the set working condition before overhaul are calculated according to the following formula;
H ms ＝H(P ms ，T ms ) (3-1)
S ms ＝S(P ms ，T ms ) (3-2)
H gp ＝H(P gp ，T gp ) (3-3)
H gps ＝H(S ms ，P gp ) (3-4)
in formulae (3-1) to (3-5), H ms Representing the enthalpy value of main steam before overhaul of the steam turbine; s. the ms Representing the entropy value of main steam before overhaul of the steam turbine; h gp Representing the exhaust enthalpy value of the high-pressure cylinder before the overhaul of the steam turbine; h gps Representing the isentropic enthalpy value of the main steam to the high-pressure cylinder exhaust steam before the overhaul of the steam turbine; eta msgp Representing the efficiency of the high-pressure cylinder before the overhaul of the steam turbine; selecting 67 edition water vapor meters or 97 edition water vapor meters according to actual engineering requirements by using functions H (P, T), S (P, T) and H (S, P) used in the formulas (3-1) to (3-5);
H tj ＝H(P tj ，T tj ) (3-6)
S tj ＝S(P tj ，T tj ) (3-7)
H gpstj ＝H(S tj ，P gp ) (3-8)
in formulas (3-6) to (3-9), H tj Representing the enthalpy value of steam after an adjusting stage before overhaul of the steam turbine; s tj Representing the entropy value of steam after the adjustment stage before the overhaul of the steam turbine; h gpstj Representing the isentropic enthalpy value of the steam discharged from the steam-adjusting stage to the high-pressure cylinder before the overhaul of the steam turbine; eta tjgp Representing the efficiency of the steam turbine in the steam exhaust expansion section from the steam of the front adjusting stage to the high pressure cylinder before overhaul.
The further improvement of the invention is that in the step 5, the high-pressure cylinder efficiency and the regulation level to high-pressure cylinder steam exhaust expansion section cylinder efficiency of the steam turbine under the set working condition after overhaul are calculated according to the following formula;
H' ms ＝H(P′ ms ，T′ ms ) (5-1)
S' ms ＝S(P′ ms ，T′ ms ) (5-2)
H' gp ＝H(P′ gp ，T′ gp ) (5-3)
H' gps ＝H(S' ms ，P′ gp ) (5-4)
in formulae (5-1) to (5-5), H' ms Representing the enthalpy value of main steam after the overhaul of the steam turbine; s' ms Representing the entropy value of main steam after the overhaul of the steam turbine; h' gp Representing the steam exhaust enthalpy value of the high-pressure cylinder after the steam turbine is overhauled; h' gps Representing the isentropic enthalpy value of the main steam to the high-pressure cylinder exhaust steam after the steam turbine is overhauled; eta 'of' msgp Representing the efficiency of the high-pressure cylinder after the overhaul of the steam turbine;
H′ tj ＝H(P′ tj ，T′ tj ) (5-6)
S′ tj ＝S(P′ tj ，T′ tj ) (5-7)
H' gpstj ＝H(S′ tj ，P′ tj ) (5-8)
in formulae (5-6) to (5-9), H t ' j Representing the steam enthalpy value of the steam turbine after the overhaul and the regulation stage; s' tj Representing the steam entropy value after the steam turbine major repair and the adjusting stage; h' gpstj Representing the isentropic enthalpy value of the steam discharged from the steam turbine after the steam turbine is overhauled and the adjusting stage to the high pressure cylinder; eta 'of' tjgp Representing the efficiency of the steam turbine in the steam exhaust expansion section from the steam turbine after the overhaul and the adjusting stage to the high pressure cylinder.
The further improvement of the invention is that in step 6, the efficiency improvement percentage point of the high-pressure cylinder of the steam turbine before and after overhaul and the efficiency improvement percentage point of the steam of the regulating stage of the steam turbine before and after overhaul to the steam exhaust expansion section of the high-pressure cylinder are calculated according to the following formula;
Δη msgp ＝η' msgp -η msgp (6-1)
Δη tjgp ＝η′ tjgp -η tjgp (6-2)。
the invention is further improved in that in step 7, the single-valve to sequential-valve-cylinder efficiency individual-lifting percentage point of the steam turbine is calculated according to the following formula, and is represented by a symbol delta eta;
Δη＝Δη msgp -Δη tjgp (7-1)。
in a further development of the invention, in step 9, the heat rate correction for the steam turbine from the post-overhaul sequential valve state to the single valve state is calculated according to the formula given below, with the sign Δ HR v Represents;
ΔHR v ＝Δη×h (9-1)。
a further improvement of the present invention is that in step 10, the heat rate from the after-overhaul sequence valve state correction to the single valve state is calculated according to the following formula;
HR c ＝HR xh -ΔHR v (10-1)
HR in the formula (10-1) c Representing the heat consumption rate of the steam turbine from the state of the sequence valve after overhaul to the state of the single valve; HR (human HR) xh Representing the heat rate of the turbine after overhaul.
The invention has at least the following beneficial technical effects:
the invention provides a calculation method for correcting a steam turbine sequence valve state to a single valve state, which aims to correct the sequence valve state after overhaul to the single valve state or correct the single valve state after overhaul to the sequence valve state, so that heat consumption rate comparison of the steam turbine before and after overhaul on the same valve position control reference is facilitated, and on the contrary, the correction method for correcting the steam turbine single valve state to the sequence valve state can also be executed by referring to the invention. Therefore, the invention can realize the aim of correcting the steam turbine until the valve position reference is consistent when the valve position reference is inconsistent before and after the steam turbine is overhauled.
Drawings
FIG. 1 is a schematic diagram of enthalpy entropy for the present invention;
description of the reference numerals:
ms, main steam, tj, adjusting stage rear steam, gp and high-pressure cylinder exhaust steam.
Detailed Description
Exemplary embodiments of the present invention will be described in more detail below with reference to the accompanying drawings. While exemplary embodiments of the invention are shown in the drawings, it should be understood that the invention may be embodied in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the invention to those skilled in the art. It should be noted that the embodiments and features of the embodiments of the present invention may be combined with each other without conflict. The present invention will be described in detail below with reference to the accompanying drawings in conjunction with embodiments.
As shown in FIG. 1, the invention provides a calculation method for correcting the sequential valve state of a steam turbine to be in a single valve state, which comprises the step of calculating the efficiency of a steam-discharging expansion section of a high-pressure cylinder after a regulating stage.
According to the calculation method for correcting the state of the sequence valve of the steam turbine to the state of the single valve, the efficiency of the steam-discharging expansion section of the steam-adjusting stage can approximately replace the efficiency of the high-pressure cylinder of the steam turbine. The lifting amount of the efficiency of the steam exhaust expansion section of the adjusting stage rear steam to the high-pressure cylinder before major repair after major repair can be considered as the effect generated by major repair.
The calculation method for correcting the state of the sequence valve of the steam turbine to the state of the single valve comprises the following steps that: the first part is the cylinder efficiency lifting amount of the sequence valve compared with a single valve; the second part is the lifting amount generated by overhaul before major overhaul after overhaul, and the second part can be replaced by the lifting amount of the cylinder efficiency of the steam-exhaust expansion section of the adjusting stage rear steam to the high-pressure cylinder before major overhaul after overhaul.
According to the calculation method for correcting the state of the sequence valve of the steam turbine to the state of the single valve, after the lifting amount of the cylinder efficiency of the steam-to-high-pressure-cylinder steam-exhaust expansion section of the regulating stage after the large repair is deducted from the lifting amount of the high-pressure-cylinder efficiency of the high-pressure-cylinder in the state of the sequence valve after the large repair than in the state of the single valve before the large repair, the rest part is the lifting amount of the cylinder efficiency of the sequence valve, which is larger than the single valve, namely the correction amount of the cylinder efficiency of the sequence valve corrected to the single valve.
The invention has the further improvement that a calculation method needs to be found to accurately calculate the absolute influence quantity of the efficiency of the high-pressure cylinder, which is increased by one percent, on the heat consumption rate of the steam turbine.
The calculation method for correcting the state of the sequence valve of the steam turbine to the state of the single valve comprises three state points: ms, main steam; tj, adjusting stage steam; gp and high-pressure cylinder exhaust.
The invention provides a calculation method for correcting the state of a sequence valve of a steam turbine to be in a single-valve state, which comprises the following steps:
step 1: it is assumed that the turbine operates under a single valve before overhaul and the turbine operates under a sequence valve after overhaul. The same applies if it is assumed that the turbine operates under single valve after overhaul, and that the turbine operates under sequence valve before overhaul. The invention uses the steam turbine before major repair to operate under a single valve, and the steam turbine after major repair to operate under a sequence valve for calculation.
Step 2: measuring main steam pressure P of steam turbine under set working condition before overhaul ms Main steam temperature T ms Regulating stageRear steam pressure P tj Regulating the post-stage steam temperature T tj Exhaust pressure P of high-pressure cylinder gp Exhaust temperature T of high-pressure cylinder gp . The units of the variables adopted by the invention all adopt an international unit system.
And step 3: and calculating the high-pressure cylinder efficiency of the steam turbine under the set working condition before overhaul and the cylinder efficiency of the steam exhaust expansion section of the regulating stage to the high-pressure cylinder according to the following formula. The set working condition is determined according to the actual engineering requirement, and can be one or more.
H ms ＝H(P ms ，T ms ) (3-1)
S ms ＝S(P ms ，T ms ) (3-2)
H gp ＝H(P gp ，T gp ) (3-3)
H gps ＝H(S ms ，P gp ) (3-4)
In formulae (3-1) to (3-5), H ms Representing the enthalpy value of main steam before overhaul of the steam turbine; s ms Representing the entropy value of main steam before overhaul of the steam turbine; h gp Representing the steam exhaust enthalpy value of the high-pressure cylinder before the overhaul of the steam turbine; h gps Representing the isentropic enthalpy value of main steam to high-pressure cylinder exhaust steam before the overhaul of the steam turbine; eta msgp Representing the high pressure cylinder efficiency before turbine overhaul. In addition, the functions H (P, T), S (P, T) and H (S, P) used in the formulas (3-1) to (3-5) can be selected from 67 version water vapor meters or 97 version water vapor meters according to the actual engineering requirements, and the following is the same. It is worth noting that: once a certain version of the steam meter is determined to be adopted, the same version of the steam meter is adopted in the whole calculation process, and the upper part and the lower part are kept consistent.
H tj ＝H(P tj ，T tj ) (3-6)
S tj ＝S(P tj ，T tj ) (3-7)
H gpstj ＝H(S tj ，P gp ) (3-8)
In formulae (3-6) to (3-9), H tj Representing the enthalpy value of steam after an adjusting stage before overhaul of the steam turbine; s tj Representing the entropy value of steam after the adjustment stage before the overhaul of the steam turbine; h gpstj Representing the isentropic enthalpy value of the steam discharged from the adjusting stage to the high pressure cylinder before the overhaul of the steam turbine; eta tjgp Representing the efficiency of the steam turbine in the steam exhaust expansion section from the steam of the front adjusting stage to the high pressure cylinder before overhaul.
And 4, step 4: measuring main steam pressure P 'of turbine under set working condition after overhaul' ms Of main steam temperature T' ms Regulated post stage steam pressure P' tj Post-regulated steam temperature T' tj Exhaust pressure P 'of high-pressure cylinder' gp Exhaust temperature T 'of high pressure cylinder' gp 。
And 5: and calculating the high-pressure cylinder efficiency of the steam turbine under the set working condition after the overhaul and the cylinder efficiency of the steam exhaust expansion section of the regulating stage to the high-pressure cylinder according to the following formula.
H' ms ＝H(P′ ms ，T′ ms ) (5-1)
S' ms ＝S(P′ ms ，T′ ms ) (5-2)
H' gp ＝H(P′ gp ，T′ gp ) (5-3)
H' gps ＝H(S' ms ，P′ gp ) (5-4)
In formulae (5-1) to (5-5), H' ms Representing the enthalpy value of main steam after the overhaul of the steam turbine; s' ms Representing the entropy value of main steam after the overhaul of the steam turbine; h' gp Representing the steam exhaust enthalpy value of the high-pressure cylinder after the steam turbine is overhauled; h' gps Representing the isentropic enthalpy value of the main steam to the high-pressure cylinder exhaust steam after the steam turbine is overhauled; eta 'of' msgp Representing the high pressure cylinder efficiency after turbine overhaul.
H′ tj ＝H(P′ tj ，T′ tj ) (5-6)
S′ tj ＝S(P′ tj ，T′ tj ) (5-7)
H' gpstj ＝H(S′ tj ，P′ tj ) (5-8)
H 'in the formulae (5-6) to (5-9)' tj Representing the steam enthalpy value of the steam turbine after the overhaul and the regulation stage; s' tj Representing the steam entropy value after the steam turbine major repair and the adjusting stage; h' gpstj Representing the isentropic enthalpy value of the steam discharged from the steam turbine after the steam turbine is overhauled and the adjusting stage to the high pressure cylinder; eta 'of' tjgp Representing the efficiency of the steam turbine in the steam exhaust expansion section from the steam turbine after the overhaul and the adjusting stage to the high pressure cylinder.
Step 6: and calculating the percentage improvement of the efficiency of the high-pressure cylinder of the steam turbine before and after overhaul and the percentage improvement of the efficiency of the steam of the regulating stage of the steam turbine before and after overhaul to the steam exhaust expansion section cylinder of the high-pressure cylinder according to the following formulas.
Δη msgp ＝η' msgp -η msgp (6-1)
Δη tjgp ＝η′ tjgp -η tjgp (6-2)
And 7: and calculating the single-valve to sequential-valve-cylinder efficiency single-lifting percentage point of the steam turbine according to the following formula, wherein the symbol delta eta represents the single-valve to sequential-valve-cylinder efficiency single-lifting percentage point.
Δη＝Δη msgp -Δη tjgp (7-1)
And step 8: and according to the type of the steam turbine, looking up relevant documents, determining the absolute influence quantity of the efficiency improvement of the high-pressure cylinder of the steam turbine by one percent on the heat consumption rate of the steam turbine, wherein the absolute influence quantity is represented by a symbol h.
And step 9: calculating the heat consumption rate correction amount of the steam turbine from the sequence valve state after the overhaul to the single valve state according to the following formula, and taking the symbol delta HR v And (4) representing.
ΔHR v ＝Δη×h (9-1)
Step 10: the heat rate from the after-overhaul sequence valve state correction to the single valve state was calculated according to the following equation.
HR c ＝HR xh -ΔHR v (10-1)
HR in the formula (10-1) c Representing the heat consumption rate of the steam turbine from the state of the sequence valve after overhaul to the state of the single valve; HR (human HR) xh Representing the heat rate of the turbine after overhaul.
Although the invention has been described in detail hereinabove with respect to a general description and specific embodiments thereof, it will be apparent to those skilled in the art that modifications or improvements may be made thereto based on the invention. Accordingly, such modifications and improvements are intended to be within the scope of the invention as claimed.
Claims (8)
1. A calculation method for correcting the sequential valve state of a steam turbine to be in a single valve state is characterized by comprising the following steps of:
step 1: setting the steam turbine to operate under a single valve before overhaul, and operating the steam turbine under a sequence valve after overhaul for calculation;
step 2: measuring main steam pressure P of steam turbine under set working condition before overhaul ms Main steam temperature T ms Post-regulation stage steam pressure P tj Regulating the post-stage steam temperature T tj Exhaust pressure P of high-pressure cylinder gp And high pressure cylinder exhaust temperature T gp ；
And 3, step 3: calculating the high-pressure cylinder efficiency of the steam turbine under a set working condition before overhaul and the cylinder efficiency of the steam exhaust expansion section of the high-pressure cylinder of the regulating stage;
and 4, step 4: measuring main steam pressure P 'of turbine under set working condition after overhaul' ms Of main steam temperature T' ms Regulated post stage steam pressure P' tj Post-regulated steam temperature T' tj Exhaust pressure P 'of high-pressure cylinder' gp And high-pressure cylinder exhaust temperature T' gp ；
And 5: calculating the high-pressure cylinder efficiency and the regulation level to high-pressure cylinder steam exhaust expansion section cylinder efficiency of the steam turbine under the set working condition after the overhaul;
step 6: calculating the efficiency improvement percentage point of the high-pressure cylinder of the steam turbine before and after overhaul and the efficiency improvement percentage point of the steam of the regulating stage of the steam turbine before and after overhaul to the steam exhaust expansion section of the high-pressure cylinder;
and 7: calculating the single improvement percentage point of the efficiency from the single valve of the steam turbine to the sequence valve cylinder, and representing the single improvement percentage point by a symbol delta eta;
and 8: according to the type of the steam turbine, relevant documents are consulted to determine the absolute influence quantity of the efficiency improvement of the high-pressure cylinder of the steam turbine on the heat consumption rate of the steam turbine, wherein the absolute influence quantity is represented by a symbol h;
and step 9: calculating the heat consumption rate correction amount of the steam turbine from the sequence valve state after the overhaul to the single valve state, and taking the symbol delta HR v Represents;
step 10: and calculating the heat consumption rate from the state of the sequence valve after the overhaul to the state of the single valve.
2. The method for calculating the state of the sequence valve of the steam turbine corrected to the state of the single valve according to claim 1, wherein in the step 2, the units of the variables are all in an international system of units.
3. The method for calculating the state of the sequence valve of the steam turbine corrected to the state of the single valve according to claim 1, wherein in the step 3, the high-pressure cylinder efficiency and the regulation stage to high-pressure cylinder exhaust expansion section cylinder efficiency of the steam turbine under the set working condition before overhaul are calculated according to the following formula;
H ms ＝H(P ms ，T ms ) (3-1)
S ms ＝S(P ms ，T ms ) (3-2)
H gp ＝H(P gp ，T gp ) (3-3)
H gps ＝H(S ms ，P gp ) (3-4)
formula (3)In (1) to (3-5), H ms Representing the enthalpy value of main steam before overhaul of the steam turbine; s ms Representing the entropy value of main steam before overhaul of the steam turbine; h gp Representing the steam exhaust enthalpy value of the high-pressure cylinder before the overhaul of the steam turbine; h gps Representing the isentropic enthalpy value of main steam to high-pressure cylinder exhaust steam before the overhaul of the steam turbine; eta msgp Representing the efficiency of the high-pressure cylinder before the overhaul of the steam turbine; selecting 67 edition water vapor meters or 97 edition water vapor meters according to actual engineering requirements by using functions H (P, T), S (P, T) and H (S, P) used in the formulas (3-1) to (3-5);
H tj ＝H(P tj ，T tj ) (3-6)
S tj ＝S(P tj ，T tj ) (3-7)
H gpstj ＝H(S tj ，P gp ) (3-8)
in formulae (3-6) to (3-9), H tj Representing the enthalpy value of steam after an adjusting stage before overhaul of the steam turbine; s tj Representing the entropy value of steam after the adjustment stage before the overhaul of the steam turbine; h gpstj Representing the isentropic enthalpy value of the steam discharged from the steam-adjusting stage to the high-pressure cylinder before the overhaul of the steam turbine; eta tjgp Representing the efficiency of the steam turbine in the steam exhaust expansion section from the steam of the front adjusting stage to the high pressure cylinder before overhaul.
4. The method for calculating the state of the sequence valve of the steam turbine corrected to the state of the single valve according to the claim 3, wherein in the step 5, the high pressure cylinder efficiency and the regulating stage to high pressure cylinder exhaust expansion section cylinder efficiency of the steam turbine under the set working condition after the overhaul are calculated according to the following formula;
H′ ms ＝H(P′ ms ，T′ ms ) (5-1)
S′ ms ＝S(P′ ms ，T′ ms ) (5-2)
H′ gp ＝H(P′ gp ，T′ gp ) (5-3)
H′ gps ＝H(S′ ms ，P′ gp ) (5-4)
in formulae (5-1) to (5-5), H' ms Representing the enthalpy value of main steam after the overhaul of the steam turbine; s' ms Representing the entropy value of main steam after the overhaul of the steam turbine; h' gp Representing the steam exhaust enthalpy value of the high-pressure cylinder after the steam turbine is overhauled; h' gps Representing the isentropic enthalpy value of the main steam to the high-pressure cylinder exhaust steam after the steam turbine is overhauled; eta 'of' msgp Representing the efficiency of the high-pressure cylinder after the overhaul of the steam turbine;
H′ tj ＝H(P′ tj ，T′ tj ) (5-6)
S′ tj ＝S(P′ tj ，T′ tj ) (5-7)
H′ gpstj ＝H(S′ tj ，P′ tj ) (5-8)
in formulae (5-6) to (5-9), H' tj Representing the steam enthalpy value of the steam turbine after the overhaul and the regulation stage; s' tj Representing the steam entropy value after the steam turbine major repair and the adjusting stage; h' gpstj Representing the isentropic enthalpy value of the steam discharged from the regulating stage to the high pressure cylinder after the overhaul of the steam turbine; eta 'of' tjgp Representing the efficiency of the steam turbine in the steam exhaust expansion section from the steam turbine after the overhaul and the adjusting stage to the high pressure cylinder.
5. The method for calculating the steam turbine sequence valve state correction to the single valve state according to claim 4, wherein in step 6, the percentage increase of the high pressure cylinder efficiency of the steam turbine before and after overhaul and the percentage increase of the cylinder efficiency of the steam turbine after the steam turbine adjustment stage to the high pressure cylinder exhaust expansion section before and after overhaul are calculated according to the following formula;
Δη msgp ＝η′ msgp -η msgp (6-1)
Δη tjgp ＝η′ tjgp -η tjgp (6-2)。
6. the method for calculating the correction of the sequential valve state of the steam turbine to the single valve state according to claim 5, wherein in the step 7, the single valve to sequential valve cylinder efficiency single lifting percentage point of the steam turbine is calculated according to the following formula, and is represented by a symbol Δ η;
Δη＝Δη msgp -Δη tjgp (7-1)。
7. the method according to claim 6, wherein in step 9, the heat rate correction amount of the steam turbine from the sequential valve state after the overhaul to the single valve state is calculated according to the following formula, and the symbol Δ HR is used as the heat rate correction amount of the steam turbine from the sequential valve state after the overhaul to the single valve state v Represents;
ΔHR v ＝Δη×h (9-1)。
8. the method according to claim 7, wherein in step 10, the heat rate from the corrected sequential valve state to the single valve state after the overhaul is calculated according to the following formula;
HR c ＝HR xh -ΔHR v (10-1)
HR in the formula (10-1) c Representing the heat consumption rate of the steam turbine from the state of the sequence valve after overhaul to the state of the single valve; HR (human HR) xh Representing the heat rate of the turbine after overhaul.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210742265.3A CN114943127B (en) | 2022-06-28 | 2022-06-28 | Calculation method for correcting sequential valve state of steam turbine to single valve state |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210742265.3A CN114943127B (en) | 2022-06-28 | 2022-06-28 | Calculation method for correcting sequential valve state of steam turbine to single valve state |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114943127A true CN114943127A (en) | 2022-08-26 |
| CN114943127B CN114943127B (en) | 2023-07-11 |
Family
ID=82910632
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210742265.3A Active CN114943127B (en) | 2022-06-28 | 2022-06-28 | Calculation method for correcting sequential valve state of steam turbine to single valve state |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN114943127B (en) |
Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102967464A (en) * | 2012-12-07 | 2013-03-13 | 山东电力集团公司电力科学研究院 | Method for evaluating performances of condensing steam turbine after high back pressure improvement |
| CN103046972A (en) * | 2012-12-13 | 2013-04-17 | 哈尔滨工业大学 | Nonlinear automatic undisturbed single valve/sequence valve switching method for steam turbine |
| US20140223896A1 (en) * | 2011-10-28 | 2014-08-14 | Beijing Xiang Tian Huachuang Aerodynamic Force Technology Research Institute Company Limited | Compressed air engine assembly with complementary compressed air circuit |
| CN104408540A (en) * | 2014-12-17 | 2015-03-11 | 国网上海市电力公司 | Assessment method of energy saving quantity of improved steam turbine |
| CN107783415A (en) * | 2017-09-30 | 2018-03-09 | 西安热工研究院有限公司 | A kind of fired power generating unit of DCS data minings determines sliding pressure operation curve computational methods |
| CN109869198A (en) * | 2019-01-23 | 2019-06-11 | 西安热工研究院有限公司 | One kind being based on the modified steam turbine life-cycle high pressure cylinder efficiency monitoring method in valve position |
| CN110222358A (en) * | 2019-04-16 | 2019-09-10 | 华电电力科学研究院有限公司 | For the modified numerical computation method of different load tubine heat consumption rate |
| CN111927570A (en) * | 2020-08-11 | 2020-11-13 | 西安热工研究院有限公司 | Steam distribution curve optimization method for undisturbed switching of single valve/sequence valve of nozzle-regulated steam turbine |
| CN112444396A (en) * | 2020-11-11 | 2021-03-05 | 西安热工研究院有限公司 | Turbine sliding pressure optimization method combining performance test and comprehensive variable working condition calculation |
| CN113486472A (en) * | 2021-07-26 | 2021-10-08 | 国能南京电力试验研究有限公司 | Method for calculating influence quantity of steam turbine cylinder efficiency on heat rate |
| CN113806680A (en) * | 2021-09-28 | 2021-12-17 | 西安热工研究院有限公司 | Method for calculating correction quantity of steam turbine inlet pressure loss to steam turbine internal efficiency |
| CN114239218A (en) * | 2021-11-09 | 2022-03-25 | 中国大唐集团科学技术研究院有限公司中南电力试验研究院 | Optimization calculation method for main steam pressure of steam turbine set under variable working conditions |
-
2022
- 2022-06-28 CN CN202210742265.3A patent/CN114943127B/en active Active
Patent Citations (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20140223896A1 (en) * | 2011-10-28 | 2014-08-14 | Beijing Xiang Tian Huachuang Aerodynamic Force Technology Research Institute Company Limited | Compressed air engine assembly with complementary compressed air circuit |
| RU2569952C1 (en) * | 2011-10-28 | 2015-12-10 | Бейжин СянТянь Хуанчуан Аэродинамик Форс Текнолоджи Рисерч Инститьют Кампани Лимитед | Air-operated engine with auxiliary compressed air circuit |
| CN102967464A (en) * | 2012-12-07 | 2013-03-13 | 山东电力集团公司电力科学研究院 | Method for evaluating performances of condensing steam turbine after high back pressure improvement |
| CN103046972A (en) * | 2012-12-13 | 2013-04-17 | 哈尔滨工业大学 | Nonlinear automatic undisturbed single valve/sequence valve switching method for steam turbine |
| CN104408540A (en) * | 2014-12-17 | 2015-03-11 | 国网上海市电力公司 | Assessment method of energy saving quantity of improved steam turbine |
| CN107783415A (en) * | 2017-09-30 | 2018-03-09 | 西安热工研究院有限公司 | A kind of fired power generating unit of DCS data minings determines sliding pressure operation curve computational methods |
| CN109869198A (en) * | 2019-01-23 | 2019-06-11 | 西安热工研究院有限公司 | One kind being based on the modified steam turbine life-cycle high pressure cylinder efficiency monitoring method in valve position |
| CN110222358A (en) * | 2019-04-16 | 2019-09-10 | 华电电力科学研究院有限公司 | For the modified numerical computation method of different load tubine heat consumption rate |
| CN111927570A (en) * | 2020-08-11 | 2020-11-13 | 西安热工研究院有限公司 | Steam distribution curve optimization method for undisturbed switching of single valve/sequence valve of nozzle-regulated steam turbine |
| CN112444396A (en) * | 2020-11-11 | 2021-03-05 | 西安热工研究院有限公司 | Turbine sliding pressure optimization method combining performance test and comprehensive variable working condition calculation |
| CN113486472A (en) * | 2021-07-26 | 2021-10-08 | 国能南京电力试验研究有限公司 | Method for calculating influence quantity of steam turbine cylinder efficiency on heat rate |
| CN113806680A (en) * | 2021-09-28 | 2021-12-17 | 西安热工研究院有限公司 | Method for calculating correction quantity of steam turbine inlet pressure loss to steam turbine internal efficiency |
| CN114239218A (en) * | 2021-11-09 | 2022-03-25 | 中国大唐集团科学技术研究院有限公司中南电力试验研究院 | Optimization calculation method for main steam pressure of steam turbine set under variable working conditions |
Non-Patent Citations (5)
| Title |
|---|
| ATANG SALAM;FAJAR PURNOMO AND WAHYU CAESARENDRA: "Comparison Study of Single Valve and Sequential Valve Mode on the Effect of Steam Turbine Heat Rate" * |
| 吴涛;付昶;: "二次再热汽轮机热力性能评价方法初探", no. 03 * |
| 徐海强;李静芬;: "准大发电厂2号汽轮机组热效率试验及分析", no. 02 * |
| 李状;郭容赫;樊芮;: "660MW汽轮机配汽方式对机组煤耗影响分析", no. 04 * |
| 郑威;郝玉振;王学栋;: "超临界压力机组低负荷滑压运行方式试验研究", no. 06 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN114943127B (en) | 2023-07-11 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US5347466A (en) | Method and apparatus for power plant simulation and optimization | |
| US8091361B1 (en) | Method and apparatus for controlling the final feedwater temperature of a regenerative Rankine cycle using an exergetic heater system | |
| CN102966385B (en) | Steam turbine plant and operation method therefor | |
| US11236640B2 (en) | Steam power plant, modification method and operation method of steam power plant | |
| US6339926B1 (en) | Steam-cooled gas turbine combined power plant | |
| CN113719325B (en) | Improved method for variable back pressure characteristic test of steam turbine | |
| US4961311A (en) | Deaerator heat exchanger for combined cycle power plant | |
| US8387356B2 (en) | Method of increasing power output of a combined cycle power plant during select operating periods | |
| CN109372594B (en) | Method for optimizing sliding pressure operation of double reheating steam turbine | |
| US20100031933A1 (en) | System and assemblies for hot water extraction to pre-heat fuel in a combined cycle power plant | |
| CN107035537B (en) | A kind of combined cycle warming-up load dynamic matching method | |
| CN109033724A (en) | Stream temperature degree applied to steam turbine sliding pressure operation consumes poor fair curve optimization method | |
| CN108843413B (en) | Method for calculating peak shaving compensation reference value of renewable energy peak shaving unit | |
| CN111507011B (en) | Method for correcting influence quantity of heat supply extraction steam on sliding pressure operation of steam turbine | |
| US20230046791A1 (en) | Installation comprising an auxiliary module | |
| CN114943127A (en) | Calculation method for correcting steam turbine sequence valve state to single valve state | |
| US20210396159A1 (en) | Exhaust gas recirculation in gas and steam turbine plants | |
| CN113158444B (en) | Correction calculation method for influence of low-temperature economizer operation on steam turbine heat consumption | |
| JP4208397B2 (en) | Start-up control device for combined cycle power plant | |
| CN113806680B (en) | Method for calculating correction amount of steam turbine internal efficiency caused by steam turbine inlet pressure loss | |
| CN106884689B (en) | A kind of method of small-sized steam-extracting type heat supply steam turbine steam discharge wet down | |
| JP2000110511A (en) | Cogeneration method and its system | |
| CN113158443B (en) | Correction calculation method for influence of high-temperature economizer operation on steam turbine heat consumption | |
| US11085336B2 (en) | Method for operating a combined cycle power plant and corresponding combined cycle power plant | |
| CN113006891A (en) | Comprehensive frequency modulation system and method for coupling heat supply and low-pressure steam extraction |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |