CN112668111B - Life design and monitoring method of steam turbine rotor under low-cycle and high-cycle fatigue - Google Patents
Life design and monitoring method of steam turbine rotor under low-cycle and high-cycle fatigue Download PDFInfo
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Abstract
The invention provides a method for designing and monitoring the service life of a steam turbine rotor under the action of low-cycle and high-cycle fatigue, which comprises the following steps: s1, obtaining the operation parameters of the turbine, the performance parameters of the turbine rotor, the crack size parameters and the total life criterion value tau0And an operating life τ; s2, calculating the theoretical total service life tau of the turbine rotor under the action of low-cycle fatigue and high-cycle fatigue in the design stage of the turbineCLt(ii) a When tau isCLt＜τ0In time, the performance parameters of the turbine rotor are optimized and tau is recalculatedCLtUp to τCLt≥τ0(ii) a S3, calculating the theoretical residual life tau of the turbine rotor under the action of low-cycle fatigue and high-cycle fatigue in the use stage of the turbineRf(ii) a When tau isRf＜(τ0- τ) operating parameters of the turbine are optimized, and τ is recalculatedRfUp to τRf＜(τ0- τ). The method and the device can be used for monitoring the total service life of crack initiation and crack propagation of the steam turbine rotor under the effects of low-cycle fatigue and high-cycle fatigue at the design stage and the use stage, and the safe service of the steam turbine rotor is ensured.
Description
Technical Field
The invention relates to the technical field of steam turbines, in particular to a method for designing and monitoring the service life of a steam turbine rotor under the action of low-cycle and high-cycle fatigue.
Background
Under the transient working condition of starting and stopping of the steam turbine, the outer surface of the rotor of the steam turbine generates crack initiation and crack propagation due to the low-cycle fatigue action caused by force load and thermal load. In the process of stable operation of the turbine under load, the outer surface of the rotor of the turbine generates crack initiation and crack propagation due to the high cycle fatigue effect caused by gravity load. Therefore, in the operation process of the steam turbine, the transient working condition of starting and load change and the loaded stable operation working condition alternately appear, the low-cycle fatigue and the high-cycle fatigue damage alternately happen to the rotor of the steam turbine, and the crack initiation and the crack propagation happen. However, at present, in the design stage and the use stage of the steam turbine, the design and the monitoring of the total service life of the crack initiation and the crack propagation of the steam turbine rotor under the action of low cycle fatigue and high cycle fatigue do not have a proper method for use.
Disclosure of Invention
In view of the above-mentioned shortcomings of the prior art, the present invention provides a method for designing and monitoring the life of a steam turbine rotor under the action of low cycle fatigue and high cycle fatigue, which monitors the total life of the steam turbine rotor under the action of low cycle fatigue and high cycle fatigue in the design stage of the steam turbine and monitors the remaining life of the steam turbine rotor under the action of low cycle fatigue and high cycle fatigue in the use stage of the steam turbine.
In order to achieve the above object, the present invention provides a method for designing and monitoring the service life of a steam turbine rotor under the action of low cycle and high cycle fatigue, comprising the following steps:
s1, obtaining the operation parameters of the turbine, the performance parameters of the turbine rotor, the crack size parameters and the total life criterion value tau0And transportA row lifetime τ;
s2, in the design stage of the steam turbine, calculating the theoretical total service life tau of the steam turbine rotor under the action of low-cycle fatigue and high-cycle fatigue according to the operation parameters of the steam turbine, the performance parameters of the steam turbine rotor and the crack size parametersCLt；
When theoretical total lifetime τCLtCriterion value tau of total life not less than0When the monitoring of the total service life of the turbine rotor is finished;
when theoretical total lifetime τCLt< Total Life criterion value tau0Optimizing the performance parameters of the turbine rotor and recalculating the theoretical total life τCLtUp to the theoretical total lifetime τCLtCriterion value tau of total life not less than0；
S3, calculating the theoretical residual life tau of the turbine rotor under the action of low-cycle fatigue and high-cycle fatigue according to the operation parameters of the turbine, the performance parameters of the turbine rotor and the crack size parameters in the use stage of the turbineRf；
When theoretical residual life τRfNot less than (total life criterion value tau)0-operating life τ), the monitoring of the remaining life of the turbine rotor is ended;
when theoretical residual life τRf< (total life criterion value tau0-operating life τ), operating parameters of the turbine are optimized and the theoretical residual life τ is recalculatedRfUp to the theoretical residual life τRfNot less than (total life criterion value tau)0-operating life τ).
Further, the operating parameters of the steam turbine include the number of cold-state annual starts ycAnnual average temperature state starting times ywAnnual average thermal state number of starts yhNumber of normal annual stoppages ynAnnual average 110% number of overspeed tests y110120% overspeed operation times y in each year120Annual average operating hours tyWorking speed n0。
Further, the performance parameters of the turbine rotor comprise mechanical performance parameters of rotor materials and a low cycle fatigue strain amplitude epsilon of the rotor under the ith working condition of the turbineaiAnd, andmaximum stress sigma of steam turbine under ith working conditionmaxi。
Further, the mechanical property parameters of the rotor material comprise the elastic modulus E of the material and the fatigue strength coefficient sigma of the materialfMaterial fatigue ductility coefficient εfLow cycle fatigue strength index b of the materialLHigh cycle fatigue strength index b of the materialHMaterial fatigue ductility index c, material fracture toughness KICLow cycle fatigue crack propagation test constant C of material0And m0High cycle fatigue crack propagation test constant C of material0HAnd m0HAnd a high cycle fatigue crack propagation threshold value of the material
Further, rotor low cycle fatigue strain amplitude epsilon of steam turbine under ith working conditionaiIncluding low cycle fatigue strain amplitude epsilon of cold start-stopacLow cycle fatigue strain range epsilon at start and stop at temperatureawLow cycle fatigue strain range epsilon of thermal start-stopah110% overspeed test low cycle fatigue strain amplitude epsilona110And 120% overspeed run low cycle fatigue strain amplitude εa120。
Further, the maximum stress sigma of the steam turbine under the ith working conditionmaxiIncluding high cycle fatigue strain amplitude epsilon in loaded operationaHRunning average stress σ under loadmNormal shutdown maximum stress σmaxn110% overspeed test maximum stress σmax110120% overrun maximum stress σmax120Maximum stress sigma of high cycle fatigue crack propagationmaxHAnd a high cycle fatigue stress range [ delta ] sigma in loaded operationH。
Further, in the step S3, the theoretical remaining life τ isRfTheoretical total life τCLt-an operating life τ.
Further, the theoretical total lifetime τCLtThe calculation method comprises the following steps in sequence:
a1, calculating annual average high cycle fatigue times y of turbine rotorH：
A2, calculating the low cycle fatigue crack initiation life N of the turbine rotor under the ith working condition of the turbinei：
NiComprises the low cycle fatigue crack initiation life N of the cold start-stop rotor of the steam turbinecLow cycle fatigue crack initiation life N of steam turbine rotor at warm start and stopwLow cycle fatigue crack initiation life N of steam turbine hot start-stop rotorh110% overspeed test rotor low cycle fatigue crack initiation life N110And 120% low cycle fatigue crack initiation life N for over-speed rotor120；
A3, calculating the high-cycle fatigue crack initiation life N of the steam turbine rotorH：
A4, calculating the crack size limit value a of the high-cycle fatigue crack propagation of the steam turbine rotorth：
Wherein M is a constant related to the crack shape parameter Q,
a、c1and theta are both crack size parameters, a is the elliptical crack minor axis radius, c1The radius of the major axis of the elliptical crack is shown, and theta is the included angle between the radial line passing through any point on the circumference of the crack and the major axis of the ellipse;
a5, calculating critical crack size a of high-cycle fatigue crack propagation of steam turbine rotorcH：
A6, calculating critical crack size a of low cycle fatigue crack propagation of steam turbine rotorci：
A7, when the minor axis radius a of the elliptical crack is not more than the crack size limit value athCalculating the first-stage low-cycle fatigue crack propagation life N of the turbine rotorfi,1：
Wherein, a0The size of the initial crack of the steam turbine rotor;
first stage low cycle fatigue crack propagation life Nfi,1Including a first stage normal shutdown low cycle fatigue crack propagation life Nfn,1First stage 110% overspeed test low cycle fatigue crack propagation life Nf110,1And a first stage 120% over-speed low cycle fatigue crack propagation life Nf120,1；
A8, when the minor axis radius a of the elliptical crack is larger than the crack size limit value athCalculating the second stage low cycle fatigue crack propagation life N of the turbine rotorfi,2：
Second stage low cycle fatigue crack propagation life Nfi,2Including second stage Normal shutdown Low cycle fatigue crack propagation Life Nfn,2110% overspeed test low cycle fatigue crack propagation life Nf110,2And a second stage 120% over-speed run low cycle fatigue crack propagation life Nf120,2；
A9 calculating the high-cycle fatigue crack propagation life N of the rotor of the steam turbinefH：
A10, calculating the annual low cycle fatigue and high cycle fatigue crack initiation life loss e of the steam turbine rotory0：
A11, calculating the crack initiation calendar life tau of the turbine rotor under the action of low cycle fatigue and high cycle fatigueCL0：
A12, calculating the annual average fatigue crack propagation life loss e of the first stage of the steam turbine rotory1：
A13, calculating the calendar life tau of the fatigue crack propagation of the first stage of the turbine rotorCL1：
A14, calculating the annual average fatigue crack propagation life loss e of the steam turbine rotor in the second stagey2：
A15, calculating the calendar life tau of the fatigue crack propagation of the second stage of the turbine rotorCL2：
A16, the theoretical Total Life τCLtComprises the following steps: tau isCLt＝τCL0+τCL1+τCL2。
As mentioned above, the method for designing and monitoring the service life of the steam turbine rotor under the low-cycle and high-cycle fatigue effects has the following beneficial effects:
the method monitors the total service life of the steam turbine rotor under the action of low-cycle fatigue and high-cycle fatigue at the design stage of the steam turbine and monitors the residual service life of the steam turbine rotor under the action of the low-cycle fatigue and the high-cycle fatigue at the use stage of the steam turbine, and ensures that the total service life or the residual service life of the steam turbine rotor is qualified by optimizing the performance parameters of the steam turbine rotor or the operation parameters of the steam turbine, and finally ensures the safe service of the steam turbine rotor.
Drawings
FIG. 1 is a block diagram of a system for designing and monitoring the life of a steam turbine rotor under low cycle and high cycle fatigue conditions according to the present application.
FIG. 2 is a flow chart of a method for designing and monitoring the life of a steam turbine rotor under low cycle and high cycle fatigue conditions according to the present application.
Fig. 3 is a block diagram of a computing process of the computing server in the present application.
Fig. 4 is a schematic structural view of a steam turbine rotor.
Detailed Description
The following description of the embodiments of the present invention is provided for illustrative purposes, and other advantages and effects of the present invention will become apparent to those skilled in the art from the present disclosure.
It should be understood that the structures, proportions, and dimensions shown in the drawings and described herein are for illustrative purposes only and are not intended to limit the scope of the present invention, which is defined by the claims, but rather by the claims. In addition, the terms such as "upper", "lower", "left", "right", "middle" and "one" used in the present specification are for convenience of description only and are not intended to limit the scope of the present invention, and changes or modifications of the relative relationship thereof may be made without substantial technical changes and modifications.
The application provides a method for designing and monitoring the service life of a steam turbine rotor under the low-cycle and high-cycle fatigue action, which is carried out by using a system for designing and monitoring the service life of the steam turbine rotor under the low-cycle and high-cycle fatigue action. As shown in fig. 1, the system for designing and monitoring the service life of a steam turbine rotor under the action of low-cycle and high-cycle fatigue comprises a database server 1, a calculation server 2, a web server 3 and a client browser 4, wherein the database server 1 is connected with the calculation server 2, the database server 1 is connected with the web server 3, the calculation server 2 is connected with the web server 3, and the web server 3 is connected with the client browser 4. The method for designing and monitoring the service life of the steam turbine rotor under the action of the low-cycle fatigue and the high-cycle fatigue can be written into computer software by adopting C language, run on a computing server 2 and be used for monitoring the theoretical total service life tau of the steam turbine rotor in the design stage of the steam turbine under the action of the low-cycle fatigue and the high-cycle fatigueCLtAnd the theoretical residual life tau of the steam turbine rotor in the use stage of the steam turbine under the action of low cycle fatigue and high cycle fatigueRf。
Further, as shown in fig. 2 and 3, the present invention provides a method for designing and monitoring the life of a steam turbine rotor under the action of low cycle and high cycle fatigue, comprising the following steps:
s1, obtaining the operation parameters of the turbine, the performance parameters of the turbine rotor, the crack size parameters and the total life criterion value tau0And the operating life tau, the operating parameters of the turbine, the performance parameters of the turbine rotor, the crack size parameters, the total life criterion tau0And the operating life τ are stored in the database server 1 and recalled from the database server 1 by the calculation server 2. In addition, the total life criterion value tau0Determining according to the requirements of power station owners; in general, for a steam turbine τ of a thermal power plant0For 40 years, for nuclear power plant turbines τ060 years old. Obtaining the statistical performance of the service life tau: and counting the calendar years between the first grid-connected operation day of the rotor from the turbine to the crack propagation remaining calendar life evaluation day.
Step S2, designing the steam turbineIn the stage, the calculation server 2 calculates the theoretical total service life tau of the turbine rotor under the action of low-cycle fatigue and high-cycle fatigue according to the operation parameters of the turbine, the performance parameters of the turbine rotor and the crack size parameters called from the database server 1CLt；
When theoretical total lifetime τCLtCriterion value tau of total life not less than0When the total service life of the steam turbine rotor is monitored to be qualified under the action of low-cycle fatigue and high-cycle fatigue, the total service life of the steam turbine rotor is monitored to be finished if the total service life of the steam turbine rotor is controlled under the action of the low-cycle fatigue and the high-cycle fatigue;
when theoretical total lifetime τCLt< Total Life criterion value tau0Optimizing the performance parameters of the turbine rotor and recalculating the theoretical total life τCLtUp to the theoretical total lifetime τCLtCriterion value tau of total life not less than0The monitoring of the total life of the turbine rotor is ended.
Step S3, in the using stage of the steam turbine, the calculation server 2 calculates the theoretical residual life tau of the steam turbine rotor under the action of low-cycle fatigue and high-cycle fatigue according to the operating parameters of the steam turbine, the performance parameters of the steam turbine rotor and the crack size parameters called from the database server 1Rf；
When theoretical residual life τRfNot less than (total life criterion value tau)0The operation life tau) shows that the residual life monitoring of the steam turbine rotor under the interaction of the low cycle fatigue and the high cycle fatigue of the original scheme is qualified, and shows that the residual life of the steam turbine rotor under the interaction of the low cycle fatigue and the high cycle fatigue is in a controlled state, so that the residual life monitoring of the steam turbine rotor is finished;
when theoretical residual life τRf< (total life criterion value tau0-operating life τ), operating parameters of the turbine are optimized and the theoretical residual life τ is recalculatedRfUp to the theoretical residual life τRfNot less than (total life criterion value tau)0-operating life τ), the monitoring of the remaining life of the turbine rotor is ended.
Therefore, the total service life of the steam turbine rotor under the action of the low-cycle fatigue and the high-cycle fatigue is monitored in the design stage of the steam turbine, the residual service life of the steam turbine rotor under the action of the low-cycle fatigue and the high-cycle fatigue is monitored in the use stage of the steam turbine, the total service life or the residual service life of the steam turbine rotor is qualified by optimizing the performance parameters of the steam turbine rotor or the operation parameters of the steam turbine, and finally the safe service of the steam turbine rotor is ensured.
The following preferred embodiment of a method for designing and monitoring the life of a steam turbine rotor under the action of low cycle and high cycle fatigue is provided, as shown in fig. 2 and 3, which specifically comprises the following steps:
first step, number of cold-state starting times of yearcAnnual average temperature state starting times ywAnnual average thermal state number of starts yhNumber of normal annual stoppages ynAnnual average 110% number of overspeed tests y110120% overspeed operation times y in each year120Annual average operating hours tyAnd an operating speed n0The operating parameters of these turbines are entered into the database server 1.
Secondly, inputting the mechanical property parameters of the rotor material into a database server 1, wherein the mechanical property parameters of the rotor material comprise the elastic modulus E and the fatigue strength coefficient sigma of the materialfMaterial fatigue ductility coefficient εfLow cycle fatigue strength index b of the materialLHigh cycle fatigue strength index b of the materialHMaterial fatigue ductility index c, material fracture toughness KICLow cycle fatigue crack propagation test constant C of material0And m0High cycle fatigue crack propagation test constant C of material0HAnd m0HAnd a high cycle fatigue crack propagation threshold value of the material
Thirdly, the low cycle fatigue strain amplitude epsilon of the rotor under the ith working condition of the steam turbineaiAnd maximum stress sigma of steam turbine under ith working conditionmaxiInto the database server 1. Wherein, the rotor low cycle fatigue of the steam turbine under the ith working condition is satisfiedAmplitude variation epsilonaiIncluding low cycle fatigue strain amplitude epsilon of cold start-stopacLow cycle fatigue strain range epsilon at start and stop at temperatureawLow cycle fatigue strain range epsilon of thermal start-stopah110% overspeed test low cycle fatigue strain amplitude epsilona110And 120% overspeed run low cycle fatigue strain amplitude εa120. Maximum stress sigma of steam turbine under ith working conditionmaxiIncluding high cycle fatigue strain amplitude epsilon in loaded operationaHRunning average stress σ under loadmNormal shutdown maximum stress σmaxn110% overspeed test maximum stress σmax110120% overrun maximum stress σmax120Maximum stress sigma of high cycle fatigue crack propagationmaxHAnd a high cycle fatigue stress range [ delta ] sigma in loaded operationH。
Fourthly, calculating annual average high cycle fatigue times y of the steam turbine rotorH：
In the above formula (1), tyThe annual average number of operating hours, n, of the steam turbine0The operating speed of the turbine.
Fifthly, calculating the low cycle fatigue crack initiation life N of the steam turbine rotor under the ith working condition of the steam turbinei：
In the above formula (2), epsilonaiThe low cycle fatigue strain amplitude of the rotor under the ith working condition of the steam turbine, E is the elastic modulus of the material of the rotor of the steam turbine, sigmafIs the material fatigue strength coefficient of the turbine rotorfIs the material fatigue ductility coefficient of the turbine rotor, bLThe low cycle fatigue strength index of the material of the steam turbine rotor, and c is the fatigue ductility index of the material of the steam turbine rotor. Thus, NiThe method comprises the following steps: low cycle fatigue crack initiation life N of steam turbine cold start-stop rotorc: according to cold stateFatigue strain amplitude epsilon of low-cycle stopacCalculating; low cycle fatigue crack initiation life N of steam turbine rotor at warm start and stopw: according to the low cycle fatigue strain amplitude epsilon of the start and stop at the temperature stateawCalculating; low cycle fatigue crack initiation life N of steam turbine hot start-stop rotorh: according to the low cycle fatigue strain amplitude epsilon of the hot start and stopahCalculating; 110% overspeed test rotor low cycle fatigue crack initiation life N110: according to 110% overspeed test low cycle fatigue strain amplitude epsilona110Calculating; 120% overspeed rotor low cycle fatigue crack initiation life N120: according to 120% overspeed operation low cycle fatigue strain amplitude epsilona120And (4) calculating.
Sixthly, calculating the high-cycle fatigue crack initiation life N of the steam turbine rotorH：
In the above formula (3), epsilonaHHigh cycle fatigue strain amplitude, sigma, for a steam turbine rotor operating under loadmMean stress of the rotor for loaded operation of the turbine, bHThe high cycle fatigue strength index of the material of the steam turbine rotor.
Seventhly, calculating the crack size limit value a of the high-cycle fatigue crack propagation of the steam turbine rotorth：
In the above-mentioned formula (4),
a high cycle fatigue crack propagation threshold, Δ σ, for rotor materialsHThe stress range of the high cycle fatigue crack propagation of the rotor under the load operation condition of the steam turbine, M is a constant related to a crack shape parameter Q,
a、c1and theta are both crack size parameters, a is the elliptical crack minor axis radius, c1The radius of the major axis of the elliptical crack is shown, and theta is the included angle between the radial line passing through any point on the circumference of the crack and the major axis of the ellipse. Typically, during the design phase of the turbine, the crack size parameters a, c1And θ can be assumed from past crack sizes, or from engineering experience; crack size parameters a, c during the service phase of the turbine1And theta is measured.
Eighthly, calculating the critical crack size a of the high-cycle fatigue crack propagation of the steam turbine rotorcH：
In the above formula (5), σmaxHMaximum stress for high cycle fatigue crack propagation, KICThe fracture toughness of the turbine rotor material.
Ninth, calculating the critical crack size a of the low cycle fatigue crack propagation of the steam turbine rotorci：
In the above-mentioned formula (6),
high cycle fatigue crack propagation threshold, σ, for rotor materialsmaxiIs the maximum stress, sigma, of the turbine under the i-th working conditionmaxiIncluding normal shutdown maximum stress σmaxn110% overspeed test maximum stress σmax110120% overrun maximum stress σmax120。
Tenth step, calculating the first-stage low-cycle fatigue crack propagation life N of the steam turbine rotorfi,1：
Elliptical crack minor axis radius in steam turbine rotorsa is not greater than the crack size limit value athIn the first stage of fatigue crack propagation of the rotor, the crack of the turbine rotor is initiated from the initial crack a0Crack size limit a to high cycle fatigue crack propagationthFirst stage low cycle fatigue crack propagation life Nfi,1The calculation formula of (2) is as follows:
in the above formula (7), a0In the case where no flaw is found in the flaw detection for the size of the initial flaw (or flaw) of the steam turbine rotor, assume that a0＝2mm；C0、m0Is a low cycle fatigue crack propagation test constant of the rotor material; sigmamaxiMaximum stress sigma for normal shutdownmaxn110% overspeed test maximum stress σmax110120% overrun maximum stress σmax120. Thus, the first stage low cycle fatigue crack propagation life Nfi,1The method comprises the following steps: first stage normal shutdown low cycle fatigue crack propagation life Nfn,1According to normal shutdown maximum stress σmaxnCalculating; first stage 110% overspeed test Low cycle fatigue crack propagation Life Nf110,1According to 110% overspeed test maximum stress σmax110Calculating; 120% over-speed run low cycle fatigue crack propagation life N in the first stagef120,1According to 120% overrun maximum stress σmax120And (4) calculating.
The eleventh step of calculating the second-stage low-cycle fatigue crack propagation life N of the steam turbine rotorfi,2：
The minor axis radius a of the elliptical crack of the steam turbine rotor is larger than the crack size limit value athIn the second stage of the rotor fatigue crack propagation, the crack size limit value a of the turbine rotor crack propagation from the high cycle fatigue crack during the on-load operation of the turbinethCritical crack size a to low cycle fatigue crack propagationciSecond stage of low cycle fatigue crack propagation life Nfi,2The calculation formula of (2) is as follows:
in the above formula (8), aciCritical crack size for low cycle fatigue crack propagation for turbine i type of operating condition; sigmamaxiMaximum stress sigma for normal shutdownmaxn110% overspeed test maximum stress σmax110120% overrun maximum stress σmax120. Thus, the second stage low cycle fatigue crack propagation life Nfi,2The method comprises the following steps: second stage Normal shutdown Low cycle fatigue crack propagation Life Nfn,2According to normal shutdown maximum stress σmaxnCalculating; second stage 110% overspeed test Low cycle fatigue crack propagation Life Nf110,2According to 110% overspeed test maximum stress σmax110Calculating; 120% over-speed run low cycle fatigue crack propagation life N in the second stagef120,2According to 120% overrun maximum stress σmax120And (4) calculating.
Twelfth step, calculating the high cycle fatigue crack propagation life N of the steam turbine rotorfH：
The minor axis radius a of the elliptical crack of the steam turbine rotor is larger than the crack size limit value athIn a second stage of fatigue crack propagation of the rotor, a crack size limit value of the crack propagation of the steam turbine rotor from the high cycle fatigue cracka thCritical crack size a to high cycle fatigue crack propagationcHHigh cycle fatigue crack propagation life NfHReferred to as high cycle fatigue crack propagation life when the turbine is operating under load.
In the above formula (9), acHCritical crack size for rotor high cycle fatigue crack propagation; delta sigmaHThe stress range of the high cycle fatigue crack propagation of the rotor under the load operation condition of the steam turbine; c0H、m0HAnd the low cycle fatigue crack propagation test constant of the rotor material.
Step eleven, calculating the annual low cycle fatigue and high cycle fatigue crack initiation life loss e of the steam turbine rotory0：
In the formula (10), y is the annual average cold-state starting frequency of the steam turbine; y iswThe annual average temperature state starting times of the steam turbine; y ishThe annual average thermal state starting times of the steam turbine; y is110The number of overspeed tests is 110% of the annual average number of the steam turbines; y is120120% overspeed operation times of the steam turbine in each year; y isHThe annual high cycle fatigue times of the steam turbine rotor; n is a radical ofcThe low cycle fatigue crack initiation life of the steam turbine cold start-stop rotor; n is a radical ofwThe low cycle fatigue crack initiation life of the steam turbine rotor at the temperature state start and stop is prolonged; n is a radical ofhThe low cycle fatigue crack initiation life of the steam turbine hot start-stop rotor; n is a radical of110The rotor low cycle fatigue crack initiation life is 110% of the overspeed test rotor; n is a radical of120The low cycle fatigue crack initiation life of the 120% overspeed operation rotor; n is a radical ofHIs the high cycle fatigue crack initiation life of the rotor.
Fourteenth step, calculating the crack initiation calendar life tau of the steam turbine rotor under the action of low cycle fatigue and high cycle fatigueCL0：
In the above formula (11), ey0The service life loss is the annual low cycle fatigue and the high cycle fatigue crack initiation.
Fifteenth step, calculating annual average fatigue crack propagation life loss e of the first stage of the steam turbine rotory1：
In the above formula (12), ynThe annual average shutdown frequency of the steam turbine; y is110The number of overspeed tests is 110% of the annual average number of the steam turbines; y is120120% overspeed operation times of the steam turbine in each year; n is a radical offn,1The service life of the rotor first-stage low-cycle fatigue crack in the shutdown process of the steam turbine is prolonged; n is a radical off110,1The service life of the first-stage low-cycle fatigue crack of the rotor in the 110% overspeed test process of the steam turbine is prolonged; n is a radical off120,1The service life of the first-stage low-cycle fatigue crack of the rotor in the 120% overspeed operation process of the steam turbine is prolonged.
Sixthly, calculating the fatigue crack propagation calendar life tau of the first stage of the steam turbine rotorCL1：
In the above formula (13), ey1The fatigue crack propagation life loss is the annual fatigue crack propagation life loss of the first stage of the steam turbine rotor.
Seventeenth step, calculating the annual average fatigue crack propagation life loss e of the steam turbine rotor in the second stagey2：
In the above formula (14), ynThe annual average shutdown frequency of the steam turbine; y is110The number of overspeed tests is 110% of the annual average number of the steam turbines; y is120120% overspeed operation times of the steam turbine in each year; y isHThe annual high cycle fatigue times of the steam turbine rotor; n is a radical offn,2The service life of the rotor low cycle fatigue crack in the second stage in the shutdown process of the steam turbine is prolonged; n is a radical off110,2The service life of the rotor low-cycle fatigue crack in the second stage in the 110% overspeed test process of the steam turbine is prolonged; n is a radical off120,2The service life of the rotor low-cycle fatigue crack in the second stage in the 120% overspeed operation process of the steam turbine is prolonged; n is a radical offHThe high cycle fatigue crack of the rotor is extended for the load operation of the steam turbine.
Eighteenth step of calculating the calendar life tau of the second stage fatigue crack propagation of the steam turbine rotorCL2：
In the above formula (15), ey2The fatigue crack propagation life loss is the second stage annual fatigue crack propagation life loss of the rotor.
Nineteenth step, theoretical Total Life τCLtComprises the following steps:
τCLt＝τCL0+τCL1+τCL2 (16)
in the above formula (16), τCL0The calendar life of the crack initiation of the steam turbine rotor under the action of low cycle fatigue and high cycle fatigue is prolonged; tau isCL1Extending the calendar life for the fatigue crack of the first stage of the steam turbine rotor; tau isCL2And (4) extending the calendar life for the second stage fatigue crack of the steam turbine rotor.
Twentieth step of determining the criterion value tau of the total service life of the crack initiation and the crack propagation of the steam turbine rotor0：
Determining the criterion value tau of the total service life of the crack initiation and crack propagation of the steam turbine rotor according to the requirements of the power station owner0For thermal power plants turbines τ in general0For 40 years, for nuclear power plant turbines τ060 years old.
Twenty-step, determining the monitoring type of the total service life of the crack initiation and the crack propagation of the steam turbine rotor:
in the design development stage and the use stage of the steam turbine, the monitoring type of the total service life of crack initiation and crack propagation of a steam turbine rotor under the action of low-cycle fatigue and high-cycle fatigue is determined according to the following conditions:
(1) in the design stage of the steam turbine, carrying out design monitoring on the total service life of crack initiation and crack propagation of a steam turbine rotor under the action of low-cycle fatigue and high-cycle fatigue, and entering the twenty-second step;
(2) and in the use stage of the steam turbine, carrying out operation monitoring on the crack initiation and crack propagation residual life of the steam turbine rotor under the action of low-cycle fatigue and high-cycle fatigue, and entering the twenty-third step.
Twenty-second step, designing and monitoring the total life of crack initiation and crack propagation under the action of low-cycle fatigue and high-cycle fatigue:
at the design stage of the steam turbine, the monitoring system of the total service life of crack initiation and crack propagation of the steam turbine rotor under the action of low-cycle fatigue and high-cycle fatigue is applied, and the optimal design control is carried out on the total service life of crack initiation and crack propagation of the steam turbine rotor under the action of low-cycle fatigue and high-cycle fatigue:
(1) if tauCLt≥τ0The monitoring of the total service life of the crack initiation and the crack propagation of the steam turbine rotor under the action of the low-cycle fatigue and the high-cycle fatigue in the original scheme is qualified, which indicates that the total service life of the crack initiation and the crack propagation of the steam turbine rotor under the action of the low-cycle fatigue and the high-cycle fatigue is in a controlled state, and the monitoring of the total service life of the crack initiation and the crack propagation of the steam turbine rotor under the action of the low-cycle fatigue and the high-cycle fatigue is finished, and the process enters the twenty-sixth step;
(2) if tauCLt＜τ0The method comprises the steps of carrying out a first step to a second step, carrying out a rotor structure improvement measure, and carrying out a first step to a second step again until tau is measuredCLt≥τ0And (4) ending the design and monitoring of the total service life of the crack initiation and crack propagation life of the steam turbine rotor under the action of low-cycle fatigue and high-cycle fatigue, and entering a twenty-sixth step.
And twenty-third step, calculating the operation life tau of the steam turbine:
and counting the calendar years between the first grid-connected operation day of the rotor and the crack propagation residual calendar life evaluation day of the rotor, namely the operation life tau.
Twenty-fourth step, calculating residual service life tau of turbine rotorRf：
τRf＝(τCL0+τCL1+τCL2)-τ (17)
Twenty-fifth step: and (3) monitoring the operation of the residual life under the action of low-cycle fatigue and high-cycle fatigue:
in the use stage of the steam turbine rotor, a monitoring system of the total service life of the low-cycle fatigue and high-cycle fatigue crack initiation and crack propagation of the steam turbine rotor is applied to carry out optimized operation control on the residual service life of the steam turbine rotor under the action of the low-cycle fatigue and the high-cycle fatigue:
(1) if tauRf≥(τ0Tau) year, the operation monitoring of the residual life of the rotor under the interaction of low-cycle fatigue and high-cycle fatigue is qualified, the residual life of the turbine rotor under the interaction of low-cycle fatigue and high-cycle fatigue is indicated to be in a controlled state, the operation monitoring of the residual life of the turbine rotor under the interaction of low-cycle fatigue and high-cycle fatigue is finished, and the twenty-sixth step is carried out;
(2) if tauRf＜(τ0Tau) year, the design monitoring of the residual life of the rotor under the interaction of low cycle fatigue and high cycle fatigue is unqualified, which shows that the annual average normal shutdown times of the steam turbine need to be optimized and improved in the operation stage, the annual average shutdown times of the steam turbine are reduced, and the first step to the twenty-fifth step are executed again until tauRf≥(τ0τ) the monitoring of the operation of the turbine rotor for the remaining life under the effect of low cycle fatigue and high cycle fatigue is over.
Twenty-sixth step of printing output result
And printing and outputting the design and monitoring results and the optimized control measures of the total service life of the crack initiation and crack propagation of the steam turbine rotor under the action of low-cycle fatigue and high-cycle fatigue as required. Therefore, a printer is also required to be configured, and the printer is connected to the calculation server 2.
In conclusion, the invention provides a method and a system for monitoring the total service life of crack initiation and crack propagation of a steam turbine rotor under the action of low-cycle fatigue and high-cycle fatigue, and realizes quantitative evaluation, design monitoring and operation monitoring of the total service life of crack initiation and crack propagation of the steam turbine rotor under the action of low-cycle fatigue and high-cycle fatigue. In the design stage, if the design monitoring of the total service life of the crack initiation and the crack propagation of the steam turbine rotor under the interaction of the low-cycle fatigue and the high-cycle fatigue is unqualified, the total service life of the crack initiation and the crack propagation of the steam turbine rotor under the interaction of the low-cycle fatigue and the high-cycle fatigue is in a controlled state by adopting a rotor structure improvement measure, and the technical effect of monitoring the total service life of the crack initiation and the crack propagation of the steam turbine rotor under the interaction of the low-cycle fatigue and the high-cycle fatigue is achieved by using the monitoring method and the system of the total service life of the crack initiation and the crack propagation of the steam turbine rotor. In the use stage, if the operation monitoring of the residual life of the rotor under the interaction of the low-cycle fatigue and the high-cycle fatigue is unqualified, the residual life of the rotor of the steam turbine under the interaction of the low-cycle fatigue and the high-cycle fatigue is in a controlled state by reducing the annual normal shutdown times of the steam turbine, and the technical effect of controlling the residual life of the rotor of the steam turbine by using the monitoring method and the system of the total life of the rotor of the steam turbine under the interaction of the low-cycle fatigue and the high-cycle fatigue is achieved.
The following provides two preferred application embodiments of the method for designing and monitoring the service life of the steam turbine rotor under the action of low-cycle and high-cycle fatigue.
Application example I,
The structure of a welded low-pressure rotor of a 1100MW half-speed nuclear turbine of a certain model is shown in FIG. 4, and the weak part of the service life of the welded low-pressure rotor is a part B of the outer surface of the rotor. In the design stage of the steam turbine, the total service life of the steam turbine rotor under the action of low-cycle fatigue and high-cycle fatigue is monitored by applying the method for designing and monitoring the service life of the steam turbine rotor under the action of low-cycle fatigue and high-cycle fatigue. The power station owner requires the criterion value tau of the total service life of crack initiation and crack propagation of the inner cylinder of the steam turbine under the action of low-cycle fatigue and high-cycle fatigue060 years old.
First, the operating parameters of the steam turbine in table 1-1 are entered into the database server 1.
TABLE 1-1 operating parameters of steam turbines
| Serial number | Item | Index value |
| 1 | Number of cold-state annual starts ycOnce/ |
4 |
| 2 | Number of annual mean temperature state starts ywOnce/time | 20 |
| 3 | Number of annual average thermal state starts yhOnce/time | 75 |
| 4 | Number of annual average normal stops ynOnce/time | 99 |
| 5 | Annual average 110% number of overspeed tests y110Once/time | 1 |
| 6 | Annual average 120% number of overspeed runs y120Once/time | 0.2 |
| 7 | Number of annual average operating hours ty/h | 7000 |
| 8 | Operating speed n0/r/min | 1500 |
And secondly, inputting the material mechanical property parameters of the turbine rotor in the table 1-2 into a database server 1.
TABLE 1-2 parameters of mechanical properties of materials for steam turbine rotors
Thirdly, the low cycle fatigue strain amplitude epsilon of the rotor under the ith working condition of the steam turbine in the table 1-3aiAnd maximum stress sigma of steam turbine under ith working conditionmaxiInto the database server 1.
TABLE 1-3 rotor low cycle fatigue strain amplitude ε under i-th working condition of steam turbineaiAnd maximum stress σmaxi
| Serial number | Item | Index value |
| 1 | Low cycle fatigue strain range epsilon of cold start and stopac/％ | 0.260625 |
| 2 | Temperature state start-stop low cycle fatigue strain amplitude epsilonaw/％ | 0.258177 |
| 3 | Low cycle fatigue strain range epsilon of hot start and stopah/％ | 0.259023 |
| 4 | 110% overspeed test low cycle fatigue strain amplitude epsilona110/％ | 0.293683 |
| 5 | 120% overspeed operation low cycle fatigue strain amplitude epsilona120/％ | 0.336406 |
| 6 | High cycle fatigue strain amplitude epsilon in loaded operationaH％ | 0.005829 |
| 7 | Running mean stress sigma under loadm/h | 248.301 |
| 8 | Maximum stress sigma of normal shutdownmaxn/MPa | 458.027 |
| 9 | Maximum stress sigma of 110% overspeed testmax110/MPa | 536.224 |
| 10 | Maximum stress sigma for 120% overrunmax120/MPa | 628.200 |
| 11 | High cycle fatigue stress range delta sigma in loaded operationH/MPa | 10.052 |
Fourthly, calculating annual average high cycle fatigue times y of the steam turbine rotorH：
Fifthly, calculating the low cycle fatigue crack initiation life N of the steam turbine rotor under the ith working condition of the steam turbineiThe results are shown in tables 1 to 4 below.
TABLE 1-4 steam turbine rotor Low cycle fatigue crack initiation Life N under the ith operating mode of the steam turbinei
Sixth step, according to
Calculating the high-cycle fatigue crack initiation life N of the steam turbine rotorH：NH＝7.2712483×109。
Seventhly, calculating the crack size limit value a of the high-cycle fatigue crack propagation of the steam turbine rotorth：
Eighthly, calculating the critical crack size a of the high-cycle fatigue crack propagation of the steam turbine rotorcH：
Ninth, calculating the critical crack size a of the low cycle fatigue crack propagation of the steam turbine rotorci：
Tenth step, calculating the first-stage low-cycle fatigue crack propagation life N of the steam turbine rotorfi,1：
The eleventh step of calculating the second-stage low-cycle fatigue crack propagation life N of the steam turbine rotorfi,2：
The results of the ninth to tenth steps are shown in tables 1-5 below:
tables 1 to 5
Twelfth step, calculating the high cycle fatigue crack propagation life N of the steam turbine rotorfH：
Step eleven, calculating the annual low cycle fatigue and high cycle fatigue crack initiation life loss e of the steam turbine rotory0：
Fourteenth step, calculating the crack initiation calendar life tau of the steam turbine rotor under the action of low cycle fatigue and high cycle fatigueCL0：
Fifteenth step, calculating annual average fatigue crack propagation life loss e of the first stage of the steam turbine rotory1：
Sixthly, calculating the fatigue crack propagation calendar life tau of the first stage of the steam turbine rotorCL1：
Seventeenth step, calculating the annual average fatigue crack propagation life loss e of the steam turbine rotor in the second stagey2：
Eighteenth step of calculating the calendar life tau of the second stage fatigue crack propagation of the steam turbine rotorCL2：
Nineteenth step, theoretical Total Life τCLtComprises the following steps:
τCLt＝τCL0+τCL1+τCL2。
the calculation results of the thirteenth to nineteenth steps are shown in tables 1 to 6 below:
tables 1 to 6
Twentieth step of determining the criterion value tau of the total service life of the crack initiation and the crack propagation of the steam turbine rotor0：
The 1100MW nuclear power turbine tau060 years old.
Twenty-step, determining the monitoring type of the total service life of the crack initiation and the crack propagation of the steam turbine rotor:
(1) in the embodiment 1, the design monitoring of the total service life of the steam turbine rotor, i.e., the crack initiation and the crack propagation under the action of the low-cycle fatigue and the high-cycle fatigue, is carried out, so that the following twenty-second step is carried out;
(2) in this example 1, the operation monitoring of the remaining life of the steam turbine rotor for crack initiation and crack propagation under the low cycle fatigue and high cycle fatigue is not performed, and therefore, the twenty-third step described below is not performed.
Twenty-second step, designing and monitoring the total life of crack initiation and crack propagation under the action of low-cycle fatigue and high-cycle fatigue:
due to tauCLt55.92 years < tau060 years, the overall life monitoring of crack initiation and crack propagation of the steam turbine rotor in the original scheme is unqualified under the action of low-cycle fatigue and high-cycle fatigue, which indicates that the structure of the steam turbine rotor needs to be optimized and improved in the design stage, the structural improvement measure of increasing the structure fillet radius of the rotor surface is adopted, the first step to the twenty-second step are executed again, the life design monitoring result of the steam turbine welded low-pressure rotor after the structural improvement is listed in the following tables 1-7, and the tau is up to this pointCLt74.46 years > tau0The total service life of the steam turbine rotor under the action of low cycle fatigue and high cycle fatigue is 60 yearsAnd (5) ending the design monitoring, and entering the twenty-sixth step.
Tables 1 to 7
| Serial number | Item | Calculation results |
| 1 | Fatigue crack initiation life loss ey0/％ | 9.1804 |
| 2 | Fatigue crack initiation calendar life τCL0Year/year | 10.89 |
| 3 | First stage annual average fatigue crack propagation life loss ey1/％ | 1.5906 |
| 4 | First stage fatigue crack propagation calendar life τCL1Year/year | 62.87 |
| 5 | Second stage annual average fatigue crack propagation life loss ey2/％ | 142.3356 |
| 6 | Second stage fatigue crack propagation calendar life τCL2Year/year | 0.70 |
| 7 | Total life tau under low cycle fatigue and high cycle fatigueCLtYear/year | 74.46 |
Twenty-sixth step of printing output result
And printing out the design and monitoring results of monitoring the total service life of crack initiation and crack propagation of the turbine welding low-pressure rotor under the action of low-cycle fatigue and high-cycle fatigue and optimizing control measures according to the requirements.
By using the method and the system for monitoring the total service life of the crack initiation and the crack propagation of the turbine rotor under the action of the low-cycle fatigue and the high-cycle fatigue, the quantitative evaluation and the design monitoring of the total service life of the crack initiation and the crack propagation of the 1100MW turbine welded low-pressure rotor under the action of the low-cycle fatigue and the high-cycle fatigue are realized. In the design stage, the design monitoring of the total service life of crack initiation and crack propagation of the steam turbine rotor under the interaction of low-cycle fatigue and high-cycle fatigue in the original design scheme is unqualified, and the total service life of crack initiation and crack propagation of the steam turbine welding low-pressure rotor under the action of low-cycle fatigue and high-cycle fatigue exceeds 60 years by adopting a structural improvement measure for increasing the radius of a structural fillet on the surface of the rotor, so that the technical effect of monitoring the total service life of crack initiation and crack propagation of the steam turbine welding low-pressure rotor by using the monitoring method and the monitoring system of the total service life of crack initiation and crack propagation of the steam turbine rotor under the action of low-cycle fatigue and high-cycle fatigue is achieved.
Application examples II,
The structure of a welded low-pressure rotor of a 1100MW half-speed nuclear turbine of a certain model is shown in FIG. 4, and the weak part of the service life of the welded low-pressure rotor is a part B of the outer surface of the rotor. During the use stage of the steam turbine, the steam turbine rotor related to the invention is applied to the low circumferenceThe method for designing and monitoring the service life of the steam turbine rotor under the action of the high cycle fatigue monitors the crack initiation and crack propagation residual service life of the steam turbine rotor under the action of the low cycle fatigue and the high cycle fatigue. The power station owner requires the criterion value tau of the total service life of crack initiation and crack propagation of the inner cylinder of the steam turbine under the action of low-cycle fatigue and high-cycle fatigue060 years old.
First, the operating parameters of the steam turbine in table 2-1 are entered into the database server 1.
TABLE 2-1 operating parameters of steam turbines
| Serial number | Item | Index value |
| 1 | Number of cold-state annual starts ycOnce/ |
4 |
| 2 | Number of annual mean temperature state starts ywOnce/time | 20 |
| 3 | Number of annual average thermal state starts yhOnce/time | 75 |
| 4 | Number of annual average normal stops ynOnce/time | 99 |
| 5 | Annual average 110% number of overspeed tests y110Once/time | 1 |
| 6 | Annual average 120% number of overspeed runs y120Once/time | 0.2 |
| 7 | Number of annual average operating hours ty/h | 7000 |
| 8 | Operating speed n0/r/min | 1500 |
And secondly, inputting the material mechanical property parameters of the turbine rotor in the table 2-2 into the database server 1.
TABLE 2-2 parameters of mechanical properties of materials for steam turbine rotors
Thirdly, the low cycle fatigue strain amplitude epsilon of the rotor under the ith working condition of the steam turbine in the table 2-3aiAnd maximum stress sigma of steam turbine under ith working conditionmaxiInto the database server 1.
TABLE 2-3 rotor Low cycle fatigue Strain ε in turbine i-th operating modeaiAnd maximum stress σmaxi
| Serial number | Item | Index value |
| 1 | Low cycle fatigue strain range epsilon of cold start and stopac/％ | 0.260625 |
| 2 | Temperature state start-stop low cycle fatigue strain amplitude epsilonaw/％ | 0.258177 |
| 3 | Low cycle fatigue strain range epsilon of hot start and stopah/％ | 0.259023 |
| 4 | 110% overspeed test low cycle fatigue strain amplitude epsilona110/％ | 0.293683 |
| 5 | 120% overspeed operation low cycle fatigue strain amplitude epsilona120/％ | 0.336406 |
| 6 | High cycle fatigue strain amplitude epsilon in loaded operationaH％ | 0.005829 |
| 7 | Running mean stress sigma under loadm/h | 248.301 |
| 8 | Maximum stress sigma of normal shutdownmaxn/MPa | 458.027 |
| 9 | Maximum stress sigma of 110% overspeed testmax110/MPa | 536.224 |
| 10 | Maximum stress sigma for 120% overrunmax120/MPa | 628.200 |
| 11 | High cycle fatigue stress range delta sigma in loaded operationH/MPa | 10.052 |
Fourthly, calculating annual average high cycle fatigue times y of the steam turbine rotorH：
Fifthly, calculating the low cycle fatigue crack initiation life N of the steam turbine rotor under the ith working condition of the steam turbineiThe results are shown in tables 2 to 4 below.
TABLE 2-4 steam turbine rotor Low cycle fatigue crack initiation Life N under the ith operating mode of the steam turbinei
| Serial number | Working conditions | Crack initiation life NiOnce/time |
| 1 | Cold start-stop low cycle fatigue | Nc＝18903 |
| 2 | Low cycle fatigue of starting, stopping and starting at warm state | Nw＝20552 |
| 3 | Low cycle fatigue of hot start and stop | Nh＝19944 |
| 4 | 110% overspeed test low cycle fatigue | N110＝6902 |
| 5 | 120% overspeed operation low cycle fatigue | N120＝2584 |
Sixth step, according to
Calculating the high-cycle fatigue crack initiation life N of the steam turbine rotorH：NH＝7.2712483×109。
Seventhly, calculating the crack size limit value a of the high-cycle fatigue crack propagation of the steam turbine rotorth：
Eighthly, calculating the critical crack size a of the high-cycle fatigue crack propagation of the steam turbine rotorcH：
Ninth, calculating the critical crack size a of the low cycle fatigue crack propagation of the steam turbine rotorci：
Tenth step, calculating the first-stage low-cycle fatigue crack propagation life N of the steam turbine rotorfi,1：
The eleventh step of calculating the second-stage low-cycle fatigue crack propagation life N of the steam turbine rotorfi,2：
The results of the ninth to tenth steps are shown in tables 2-5 below:
tables 2 to 5
Twelfth step, calculating the high cycle fatigue crack propagation life N of the steam turbine rotorfH：
Step eleven, calculating the annual low cycle fatigue and high cycle fatigue crack initiation life loss e of the steam turbine rotory0：
Fourteenth step, calculating the crack initiation calendar life tau of the steam turbine rotor under the action of low cycle fatigue and high cycle fatigueCL0：
Fifteenth step, calculating annual average fatigue crack propagation life loss e of the first stage of the steam turbine rotory1：
Sixthly, calculating the fatigue crack propagation calendar life tau of the first stage of the steam turbine rotorCL1：
Seventeenth step, calculating the annual average fatigue crack propagation life loss e of the steam turbine rotor in the second stagey2：
Eighteenth step of calculating the calendar life tau of the second stage fatigue crack propagation of the steam turbine rotorCL2：
Nineteenth step, theoretical Total Life τCLtComprises the following steps:
τCLt＝τCL0+τCL1+τCL2。
the calculation results of the thirteenth to nineteenth steps are shown in tables 2 to 6 below:
tables 2 to 6
| Serial number | Item | Calculation results |
| 1 | Fatigue crack initiation life loss ey0/％ | 9.1804 |
| 2 | Fatigue crack initiation calendar life τCL0Year/year | 10.89 |
| 3 | First stage annual average fatigue crack propagation life loss ey1/％ | 2.2563 |
| 4 | First stage fatigue crack propagation calendar life τCL1Year/year | 44.32 |
| 5 | Second stage annual average fatigue crack propagation life loss ey2/％ | 141.4610 |
| 6 | Second stage fatigue crack propagation calendar life τCL2Year/year | 0.71 |
| 7 | Total life tau under low cycle fatigue and high cycle fatigueCLtYear/year | 55.92 |
Twentieth step of determining the criterion value tau of the total service life of the crack initiation and the crack propagation of the steam turbine rotor0：
The 1100MW nuclear power turbine tau060 years old.
Twenty-step, determining the monitoring type of the total service life of the crack initiation and the crack propagation of the steam turbine rotor:
(1) in the embodiment 2, the design monitoring of the total service life of the crack initiation and crack propagation of the steam turbine rotor under the action of the low-cycle fatigue and the high-cycle fatigue is not carried out, so that the twenty-second step is not carried out;
(2) in this example 2, the operation monitoring of the remaining life of the steam turbine rotor for crack initiation and crack propagation under the low cycle fatigue and high cycle fatigue is performed, and therefore, the twenty-third step described below is performed.
And twenty-third step, calculating the operation life tau of the steam turbine:
and counting the calendar years from the first grid-connected input operation day of the 1100MW turbine to the crack propagation residual calendar life evaluation day of the low-pressure welding rotor, namely the operation life tau, wherein the low-pressure welding rotor tau of the turbine is 5 years.
Twenty-fourth step, calculating residual service life tau of turbine rotorRf：
τRf＝(τCL0+τCL1+τCL2) - τ (10.89+44.32+0.71) -5 ═ 50.92 years.
Twenty-fifth step: and (3) monitoring the operation of the residual life under the action of low-cycle fatigue and high-cycle fatigue:
due to the original schemeRf50.92 years < (τ)0And the operation monitoring of the residual life of the rotor under the interaction of low-cycle fatigue and high-cycle fatigue is unqualified (60-5) to 55 years), which shows that the annual normal shutdown times of the turbine need to be optimized and improved in the operation stage, and are determined by the y of the original schemenThe optimized and improved life monitoring results of 99 times reduction to 80 times and the first step to the twenty-fifth step are shown in tables 2-7, where tau is up to nowRf61.32 years > (τ)0And tau) 55 years, the operation monitoring of the residual life of the welded low-pressure rotor of the steam turbine under the interaction of low-cycle fatigue and high-cycle fatigue is qualified, the operation monitoring of the residual life of crack initiation and crack propagation of the welded low-pressure rotor under the interaction of low-cycle fatigue and high-cycle fatigue is finished, and the twenty-sixth step is carried out.
Tables 2 to 7
| Serial number | Item | Calculation results |
| 1 | Fatigue crack initiation life loss ey0/％ | 9.0852 |
| 2 | Fatigue crack initiation calendar life τCL0Year/year | 11.01 |
| 3 | First stage annual average fatigue crack propagation life loss ey1/％ | 1.8316 |
| 4 | First stage fatigue crack propagation calendar life τCL1Year/year | 54.60 |
| 5 | Second stage annual average fatigue crack propagation life loss ey2/％ | 141.1296 |
| 6 | Second stage fatigue crack propagation calendar life τCL2Year/year | 0.71 |
| 7 | Total life tau under low cycle fatigue and high cycle fatigueCLtYear/year | 66.32 |
Twenty-sixth step of printing output result
And printing and outputting operation monitoring results of the crack initiation and crack propagation residual life of the steam turbine rotor under the action of low-cycle fatigue and high-cycle fatigue and optimizing control measures according to requirements.
By using the method and the system for monitoring the total service life of the crack initiation and the crack propagation of the turbine rotor under the action of the low-cycle fatigue and the high-cycle fatigue, the quantitative evaluation and the residual service life monitoring of the total service life of the crack initiation and the crack propagation of the 1100MW turbine welded low-pressure rotor under the action of the low-cycle fatigue and the high-cycle fatigue are realized. In the using stage, the operation monitoring of the crack initiation and crack propagation residual life of the steam turbine rotor in the original scheme is unqualified under the interaction of low-cycle fatigue and high-cycle fatigue, and the annual average normal shutdown frequency of the steam turbine is optimized and improved by the y of the original schemenAfter the number of times is reduced to 80, the operation monitoring of the residual life of the steam turbine welding low-pressure rotor under the interaction of low-cycle fatigue and high-cycle fatigue is qualified, so that the residual life of the steam turbine welding low-pressure rotor under the interaction of the low-cycle fatigue and the high-cycle fatigue is in a controlled state, and the technical effect of controlling the residual life of the steam turbine welding low-pressure rotor by using the monitoring method and the monitoring system of the total life of crack initiation and crack propagation of the steam turbine rotor under the interaction of the low-cycle fatigue and the high-cycle fatigue is achieved.
In conclusion, the present invention effectively overcomes various disadvantages of the prior art and has high industrial utilization value.
The foregoing embodiments are merely illustrative of the principles and utilities of the present invention and are not intended to limit the invention. Any person skilled in the art can modify or change the above-mentioned embodiments without departing from the spirit and scope of the present invention. Accordingly, it is intended that all equivalent modifications or changes which can be made by those skilled in the art without departing from the spirit and technical spirit of the present invention be covered by the claims of the present invention.
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| CN114412591B (en) * | 2021-12-01 | 2023-06-09 | 上海发电设备成套设计研究院有限责任公司 | Multi-dimensional safety monitoring method and device for nuclear turbine, electronic equipment and storage medium |
| CN114412589B (en) * | 2021-12-01 | 2023-03-28 | 上海发电设备成套设计研究院有限责任公司 | Multi-target multi-dimensional multi-working-condition monitoring method for nuclear turbine |
| US11725534B2 (en) | 2021-12-01 | 2023-08-15 | Shanghai Power Equipment Research Institute Co., Ltd | Method of multi-objective and multi-dimensional online joint monitoring for nuclear turbine |
| CN114396321B (en) * | 2021-12-01 | 2023-02-03 | 上海发电设备成套设计研究院有限责任公司 | Multi-dimensional service life monitoring method of nuclear turbine |
| CN114910122A (en) * | 2022-04-15 | 2022-08-16 | 中国矿业大学 | A detection system, detection method and excavator for signs of cracks in structural parts |
| CN116776587B (en) * | 2023-06-15 | 2024-07-05 | 上海发电设备成套设计研究院有限责任公司 | Nuclear turbine life-cycle stress corrosion and fatigue safety monitoring platform and method |
| CN116776589B (en) * | 2023-06-15 | 2024-11-05 | 上海发电设备成套设计研究院有限责任公司 | Long-life monitoring method for stress corrosion and fatigue of nuclear power steam turbines throughout their life cycle |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104481601A (en) * | 2014-09-15 | 2015-04-01 | 上海发电设备成套设计研究院 | Monitoring method of crack propagation life of low-cycle fatigue and high-cycle fatigue of steam turbine rotor |
| CN105781632A (en) * | 2016-02-26 | 2016-07-20 | 上海发电设备成套设计研究院 | Monitoring for total calendar life of turbine part under low-cycle fatigue and creep effect |
| CN108913854A (en) * | 2018-09-06 | 2018-11-30 | 中国科学院金属研究所 | A kind of gradient nano structure with excellent comprehensive high week and low cycle fatigue property |
| CN109255202A (en) * | 2018-11-01 | 2019-01-22 | 上海工程技术大学 | A kind of predictor method for mechanical component fatigue crack initiation life |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7328625B2 (en) * | 2005-04-28 | 2008-02-12 | Caterpillar Inc. | Systems and methods for determining fatigue life |
| CN102589867B (en) * | 2012-02-28 | 2014-06-25 | 上海发电设备成套设计研究院 | Method and device for monitoring high-cycle fatigue life of steam turbine integral rotor |
-
2020
- 2020-12-18 CN CN202011504351.8A patent/CN112668111B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104481601A (en) * | 2014-09-15 | 2015-04-01 | 上海发电设备成套设计研究院 | Monitoring method of crack propagation life of low-cycle fatigue and high-cycle fatigue of steam turbine rotor |
| CN105781632A (en) * | 2016-02-26 | 2016-07-20 | 上海发电设备成套设计研究院 | Monitoring for total calendar life of turbine part under low-cycle fatigue and creep effect |
| CN108913854A (en) * | 2018-09-06 | 2018-11-30 | 中国科学院金属研究所 | A kind of gradient nano structure with excellent comprehensive high week and low cycle fatigue property |
| CN109255202A (en) * | 2018-11-01 | 2019-01-22 | 上海工程技术大学 | A kind of predictor method for mechanical component fatigue crack initiation life |
Non-Patent Citations (2)
| Title |
|---|
| 核电汽轮机转子在低周疲劳与高周疲劳交互作用下裂纹扩展寿命的研究;史进渊;《机械工程学报》;20151130;第51卷(第22期);第152-158页 * |
| 汽轮机高温部件总寿命的计算方法及工程验证;史进渊;《动力工程学报》;20181130;第38卷(第11期);第886-918页 * |
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