CN117669141A - Design monitoring method and device for axial dynamic and static impact grinding safety of flexible operation steam turbine - Google Patents
Design monitoring method and device for axial dynamic and static impact grinding safety of flexible operation steam turbine Download PDFInfo
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Abstract
The invention provides a design monitoring method and device for axial dynamic and static impact grinding safety of a flexible operation steam turbine. The method comprises the following steps: acquiring axial dynamic and static clearance monitoring data of each stage of moving blades of a key component of the steam turbine under a target working condition; obtaining an axial dynamic and static clearance design limit value of each stage of moving blade of a key component; determining design monitoring data of key components based on the axial dynamic and static clearance monitoring data and an axial dynamic and static clearance design limit value aiming at each stage of moving blades; based on design monitoring data, structural optimization is performed on key components of the steam turbine. Therefore, the axial dynamic and static impact grinding safety of the steam turbine is in a controlled state under the target working condition, and the long service life and high flexibility of the design of the steam turbine are ensured.
Description
Technical Field
The disclosure relates to the technical field of steam turbines, in particular to a method and a device for flexibly operating axial dynamic and static impact grinding safety design monitoring of a steam turbine.
Background
Because renewable energy sources such as wind energy, solar energy and the like generate electricity with the problems of intermittence, randomness, volatility and the like, a power grid can only usually accommodate 15% of unstable power sources, and the phenomena of wind discarding and light discarding are serious. In the prior art, the peak shaving minimum load is usually 35% of rated power. Through the turbine of design control high flexibility to realize degree of depth peak shaving to 20% rated power and have the quick start climbing function, the electric wire netting just can increase the unsteady power of holding corresponding turbine rated power 15%, helps solving and abandons wind and abandons the light problem.
Disclosure of Invention
The present disclosure aims to solve, at least to some extent, one of the technical problems in the related art.
Therefore, a first object of the present disclosure is to provide a design and monitoring method for flexibly operating axial dynamic and static impact grinding safety of a steam turbine, so as to realize that the safety of key components of the steam turbine is in a controlled state under a target working condition, and ensure long service life and high flexibility of the design of the steam turbine.
A second object of the present disclosure is to provide a design and monitoring device for flexibly operating axial dynamic and static impact grinding safety of a steam turbine.
A third object of the present disclosure is to propose an electronic device.
A fourth object of the present disclosure is to propose a computer readable storage medium.
A fifth object of the present disclosure is to propose a computer programme product.
To achieve the above objective, an embodiment of a first aspect of the present disclosure provides a method for monitoring design of axial dynamic and static impact grinding safety of a flexibly operating steam turbine, including: acquiring axial dynamic and static clearance monitoring data of each stage of moving blades of a key component of the steam turbine under a target working condition; acquiring an axial dynamic and static clearance design limit value of each stage of moving blade of the key component; determining design monitoring data of the key component according to the axial dynamic and static clearance monitoring data and the axial dynamic and static clearance design limit value aiming at each stage of moving blades; and carrying out structural optimization on key components of the steam turbine based on the design monitoring data.
To achieve the above object, an embodiment of a second aspect of the present disclosure provides a safety design monitoring device for flexibly operating an axial dynamic and static impact mill of a steam turbine, including: the first acquisition module is used for acquiring axial dynamic and static clearance monitoring data of each stage of moving blades of the key component of the steam turbine under the target working condition; the second acquisition module is used for acquiring an axial dynamic and static clearance design limit value of each stage of moving blades of the key component; the determining module is used for determining design monitoring data of the key component according to the axial dynamic and static clearance monitoring data and the axial dynamic and static clearance design limit value aiming at each stage of moving blades; and the optimization module is used for carrying out structural optimization on the key components of the steam turbine based on the design monitoring data.
To achieve the above object, an embodiment of a third aspect of the present disclosure provides an electronic device, including: a processor; and a memory communicatively coupled to the processor; the memory stores computer-executable instructions; the processor executes the computer-executed instructions stored in the memory, so that the processor can execute the method for flexibly operating the turbine axial dynamic static impact grinding safety design monitoring method according to the embodiment of the first aspect.
To achieve the above object, a fourth aspect of the present disclosure provides a computer-readable storage medium having stored thereon a computer program, where the computer instructions are configured to cause the computer to execute the method for flexibly operating turbine axial dynamic and static impact grinding safety design monitoring according to the embodiment of the above aspect.
To achieve the above object, a fifth aspect of the present disclosure provides a computer program product, which includes a computer program, where the computer program when executed by a processor implements the method for monitoring the axial dynamic and static impact grinding safety design of a flexibly operating steam turbine according to the embodiment of the above aspect.
The design monitoring method and device for the axial dynamic and static impact grinding safety of the flexibly-operated steam turbine are provided by the disclosure.
Additional aspects and advantages of the disclosure will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the disclosure.
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The foregoing and/or additional aspects and advantages of the present disclosure will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings, in which:
FIG. 1 is a schematic flow chart of a design monitoring method for axial dynamic and static impact grinding safety of a flexibly operated steam turbine according to an embodiment of the present disclosure;
FIG. 2 is a schematic diagram of an apparatus for monitoring a steam turbine according to an embodiment of the present disclosure;
FIG. 3 is a schematic flow chart of another design monitoring method for axial dynamic and static impact grinding safety of a flexibly operated steam turbine according to an embodiment of the present disclosure;
FIG. 4 is a schematic flow chart of another design monitoring method for axial dynamic and static impact grinding safety of a flexibly operated steam turbine according to an embodiment of the present disclosure;
fig. 5 is a schematic structural diagram of a design monitoring device for axial dynamic and static impact grinding safety of a flexibly operated steam turbine according to an embodiment of the present disclosure.
Detailed Description
Embodiments of the present disclosure are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are exemplary and intended for the purpose of explaining the present disclosure and are not to be construed as limiting the present disclosure.
The following describes a method and a device for monitoring the design of the axial dynamic and static impact grinding safety of a flexibly-operated steam turbine according to the embodiment of the disclosure with reference to the accompanying drawings.
Fig. 1 is a schematic flow chart of a design monitoring method for axial dynamic and static impact grinding safety of a flexibly operated steam turbine according to an embodiment of the disclosure, as shown in fig. 1, the method includes the following steps:
S101, acquiring axial dynamic and static clearance monitoring data of each stage of moving blades of a key component of the steam turbine under a target working condition.
It should be noted that, in the embodiment of the present disclosure, the execution body of the method for flexibly running the axial dynamic and static impact grinding safety design monitoring method of the steam turbine is a hardware device with data processing capability and/or necessary software for driving the hardware device to work. Alternatively, the execution body may include a server, a computer, a user terminal, and other intelligent devices. Optionally, the user terminal includes, but is not limited to, a mobile phone, a computer, an intelligent voice interaction device, etc. Alternatively, the server includes, but is not limited to, a web server, an application server, a server of a distributed system, a server incorporating a blockchain, etc.
In the embodiment of the disclosure, the steam turbine is a non-positive-displacement machine which is flexibly operated, and in order to realize long service life and high flexibility of the steam turbine, design monitoring and operation monitoring can be performed under multiple dimensions and multiple targets.
In the disclosed embodiments, the goal of flexible turbine life is to run calendar life to 40 years with a life loss of only 0.75 (75%) of the total life. The high flexibility of the flexible operation turbine aims at 10000 times of starting, 16000 times of load variation, 250 times of starting every year and 400 times of load variation, the lowest safe and stable operation load is 20% rated power, and the load change rate of rapid starting climbing above 20% rated power exceeds 5% rated power.
In one possible implementation, the critical components of the steam turbine include a high pressure cylinder and a medium pressure cylinder.
Alternatively, the axial dynamic and static clearance monitoring data of each stage of moving blades can be obtained through a turbine Digital Electro-hydraulic control system (Digital Electro-Hydraulic Control System, DEH), a turbine control system (Turbine Control System, TCS), a turbine monitoring instrument system (Turbine Supervisory Instruments, TSI) and the like.
Alternatively, the target operating condition may refer to a rapid start-up and/or rapid load change hill climbing transient condition of the turbine.
Optionally, the axial dynamic and static clearance monitoring data of each stage of moving blades refers to the minimum axial dynamic and static clearance before and after each stage of moving blades, including: a first axial dynamic and static clearance minimum before the moving blade and a second axial dynamic and static clearance minimum after the moving blade.
S102, obtaining an axial dynamic and static clearance design limit value of each stage of moving blade of the key component.
Optionally, the design limit values of the axial dynamic and static gaps before and after each stage of moving blade of the high-pressure cylinder under the target working condition and the design limit values of the axial dynamic and static gaps before and after each stage of moving blade of the medium-pressure cylinder under the target working condition can be obtained.
S103, aiming at each stage of moving blade, determining design monitoring data of key components based on the axial dynamic and static clearance monitoring data and the axial dynamic and static clearance design limit value.
In the embodiment of the disclosure, the design monitoring data of the key component can be determined based on the axial dynamic and static clearance monitoring data and the axial dynamic and static clearance design limit value. That is, the ratio of the first axial running clearance minimum value to the running clearance design limit value and the ratio of the second axial running clearance minimum value to the running clearance design limit value can be used as design monitoring data of the key components.
In one possible implementation, the first axial dynamic clearance minimum before the rotor blade and the second axial dynamic clearance minimum after the rotor blade may be determined based on the axial dynamic clearance monitoring data. And further obtaining the ratio of the minimum value of the first axial dynamic and static clearance before the moving blade and the design limit value of the axial dynamic and static clearance as the axial dynamic and static clearance ratio before the moving blade. And obtaining the ratio of the minimum value of the second axial dynamic and static clearance after the moving blade to the design limit value of the axial dynamic and static clearance, and taking the ratio as the axial dynamic and static clearance ratio after the moving blade.
Further, the axial dynamic and static clearance ratio before the moving blade and the axial dynamic and static clearance ratio after the moving blade of each stage are determined as design monitoring data of key components.
S104, carrying out structural optimization on key components of the steam turbine based on the design monitoring data.
In the embodiment of the disclosure, whether the critical component of the steam turbine is qualified or not can be judged based on the design monitoring data, and if the critical component of the steam turbine is unqualified, the critical component of the steam turbine is subjected to structural optimization.
In one possible implementation manner, for each stage of moving blade of the key component, whether the minimum value of the axial dynamic and static gaps before and after the moving blade meets the monitoring qualification condition can be judged based on the axial dynamic and static gap ratio before the moving blade and the axial dynamic and static gap ratio before the moving blade. And if the minimum value of the axial dynamic and static gaps before and after the first-stage moving blade does not meet the corresponding monitoring qualification condition, carrying out structural optimization on key components of the steam turbine.
In the embodiment of the disclosure, the qualified condition for monitoring refers to the qualified condition of the minimum value of the axial dynamic and static clearance before and after each stage of moving blade of a key component of the steam turbine under the target working condition.
In one possible implementation, the design monitoring data includes a first axial dynamic-static clearance ratio before each stage of moving blade of the high pressure cylinder, and a second axial dynamic-static clearance ratio after each stage of moving blade of the high pressure cylinder. Optionally, if the first axial dynamic and static clearance ratio and the second axial dynamic and static clearance ratio are both greater than the set threshold, determining that the minimum axial dynamic and static clearance design before and after each stage of moving blade of the high-pressure cylinder under the target working condition meets the monitoring qualification condition, otherwise, not meeting the monitoring qualification condition.
In one possible implementation, the design monitoring data includes a third axial dynamic-static clearance ratio before each stage of moving blade of the intermediate pressure cylinder, and a fourth axial dynamic-static clearance ratio after each stage of moving blade of the intermediate pressure cylinder. Optionally, if the third axial dynamic and static clearance ratio and the fourth axial dynamic and static clearance ratio are both greater than the set threshold, determining that the minimum axial dynamic and static clearance designs before and after each stage of moving blade of the medium pressure cylinder under the target working condition meet the monitoring qualification condition, otherwise not meeting the monitoring qualification condition.
In one possible implementation, design monitoring data of a critical component to which the rotor blade that does not meet the monitoring qualification condition belongs is determined as the anomaly monitoring data. A structural optimization strategy set of the steam turbine is generated based on the anomaly monitoring data, wherein the structural optimization strategy set comprises at least one structural optimization improvement strategy. And carrying out structural optimization on the steam turbine according to the structural optimization strategy set, and continuously collecting design monitoring data and subsequent operation until the design monitoring data of the moving blades of each stage meet the monitoring qualification condition, and stopping structural optimization.
Alternatively, the design abnormality type of the rotor blade of the key component may be determined based on the abnormality design monitor data. And determining a structure optimization strategy set according to the type of the steam turbine and the design abnormality type of the moving blades.
In one possible implementation, after the abnormal design monitoring data is determined, generating abnormal prompt information according to the abnormal design monitoring data, the target key component to which the abnormal design monitoring data belongs and the corresponding target monitoring dimension. And acquiring the contact information of the feedback object, and sending abnormal prompt information to the feedback object according to the contact information.
In one possible implementation, the set of structure optimization policies includes one or more of the following policies: turning the axial dimension of the steam outlet side of the stator blade intermediate and the stator blade shroud and/or turning the axial dimension of the steam inlet side of the stator blade intermediate and the stator blade shroud; turning the axial dimension of the outer ring of the baffle plate and the steam outlet side of the baffle plate body and/or turning the axial dimension of the outer ring of the baffle plate and the steam inlet side of the baffle plate body; turning the axial dimension of the steam outlet side of the stator blade shroud and the stator blade intermediate of the same stage; turning the axial dimensions of the outer ring of the same-stage partition plate and the steam outlet side of the partition plate body; turning the axial dimensions of the inlet side of the stator blade shroud and the stator blade intermediate of the next stage; turning the axial dimension of the outer ring of the baffle plate at the next stage and the steam inlet side of the baffle plate body.
According to the design monitoring method for the axial dynamic and static impact grinding safety of the flexibly-operated steam turbine, design monitoring is conducted on the steam turbine, design monitoring data of minimum axial dynamic and static clearance before and after each stage of moving blades of a key part of the steam turbine under a target working condition are obtained, structural design optimization improvement is conducted on the key part of the steam turbine when the design monitoring data of minimum axial dynamic and static clearance before and after each stage of moving blades under the target working condition do not meet the monitoring qualification condition, the axial dynamic and static impact grinding safety of the moving blades of the key part of the flexibly-operated steam turbine under the target working condition is in a controlled state, and long service life and high flexibility of the design of the flexibly-operated steam turbine are guaranteed from the aspect of the minimum axial dynamic and static clearance before and after each stage of moving blades.
Fig. 2 shows a schematic view of an apparatus for monitoring a steam turbine, and the apparatus 200 includes a life monitoring module 21, a thermal stress monitoring module 22, a dynamic and static friction monitoring module 23, an optimal design module 24, an optimal operation module 25, and a data processing server 26. Wherein, life monitoring module 21, thermal stress monitoring module 22, sound bump friction monitoring module 23, optimal design module 24 and optimal operation module 25 are connected with data processing server 26. Alternatively, the apparatus 200 may be connected to a turbine digital electrohydraulic control system DEH or a turbine control system TCS, turbine monitoring instrumentation system TSI.
A life monitoring module 21 for storing minimum value deltay of axial dynamic and static clearance before each stage of moving blade fjx Minimum value deltay of axial dynamic and static clearance after each stage of moving blade bjx Axial dynamic and static clearance design limit value Y before and after each stage of moving blade of steam turbine j Wherein the subscript i represents the start-stop class of the steam turbineThe method comprises the following steps of C, H, V, 20% -100% of load fluctuation, j, I, L, k, f, b and x, wherein C represents cold start-stop, w represents warm start-stop, H represents hot start-stop, V represents polar hot start-stop, 20% -100% of load fluctuation, j represents a key component working environment, H represents high pressure, I represents medium pressure, L represents low pressure, k represents a turbine component name, V represents a valve casing, R represents a rotor, C represents a cylinder, f represents a part in front of a moving blade, b represents a moving blade, and x represents a moving blade stage number. The functions of the life monitoring module 21 include: axial dynamic and static clearance monitoring data of each stage of moving blades of a key component of the steam turbine under a target working condition.
The optimal design module 24 stores at least one monitoring abnormal data used for monitoring data according to the design of the key parts of the steam turbine under the target working condition, and performs structural optimization improvement on the key parts of the steam turbine, so that the long service life and high flexibility of the design of the steam turbine are ensured.
And the data processing server 26 is used for optimizing and improving the axial dynamic and static impact grinding safety of the steam turbine under the target working condition of the steam turbine. The obtained optimized operation measures are fed back to a digital electrohydraulic control system DEH or a TCS of the steam turbine to guide the optimized operation of the steam turbine with long service life and high flexibility.
Further, the optimization design module 24 also provides a set of structural optimization strategies including:
the design and improvement of the materials of the key parts of the steam turbine mainly comprise: the key components of the high-pressure cylinder and the medium-pressure cylinder of the steam turbine are made of materials with good mechanical properties at high temperature and long time; the key parts of the low-pressure cylinder of the steam turbine are made of materials with good stress corrosion resistance; the key parts of the steam turbine are made of materials with good low cycle fatigue performance and the like.
The key component structure design and improvement of the steam turbine mainly comprises: a whole-section rotor structure is adopted; adopting a welded rotor structure; the coal-electricity steam turbine adopts a cylinder type cylinder; the combined cycle steam turbine and the photo-thermal steam turbine adopt a thin-wall cylinder and a high-narrow flange; an electric tracing band, a heat-insulating garment and a heat-insulating structure are additionally arranged on the outer surface of the outer cylinder; avoiding adopting a structure which avoids stress concentration in a high stress area; the discontinuous part of the structure adopts the transition of a structural fillet; the radius of the structural fillet is increased, and the stress concentration coefficient is reduced; and designing a welding seam part far away from a stress concentration part and the like.
The process design and improvement of the key parts of the steam turbine mainly comprise the following steps: the toughness of the material is improved by adopting a heat treatment process; the machining precision is improved, and the machining stress concentration is eliminated; adopting a heat treatment process to reduce the residual tensile stress of welding; surface shot blasting, so that the low cycle fatigue performance is improved; turning axial dimensions of the steam outlet sides of the stator blade intermediate and the stator blade shroud of the same stage and turning axial dimensions of the steam inlet sides of the stator blade intermediate and the stator blade shroud of the next stage for the reaction turbine; for impulse turbine, turning the axial dimension of the outer ring of the same-stage baffle and the steam outlet side of the baffle body, turning the axial dimension of the outer ring of the next-stage baffle and the steam inlet side of the baffle body, and the like.
Fig. 3 is a schematic flow chart of a design monitoring method for axial dynamic and static impact grinding safety of a flexibly operated steam turbine according to an embodiment of the disclosure, as shown in fig. 3, the method includes the following steps:
s303, the axial dynamic and static gaps before and after each stage of moving blade of the key part of the steam turbine under the target working condition are designed and monitored, and the design and monitoring data of the axial dynamic and static gaps of the moving blade of the key part of the steam turbine under the target working condition are obtained.
In the embodiment of the disclosure, the design monitoring data comprises an axial dynamic and static clearance minimum value and an axial dynamic and static clearance design limit value before and after each stage of moving blades of a key part of the steam turbine under a target working condition.
In one possible implementation, the design monitoring data includes a first axial dynamic and static clearance ratio before each stage of moving blade of the high pressure cylinder, a second axial dynamic and static clearance ratio after each stage of moving blade of the high pressure cylinder, a third axial dynamic and static clearance ratio before each stage of moving blade of the medium pressure cylinder, and a fourth axial dynamic and static clearance ratio after each stage of moving blade of the medium pressure cylinder.
Optionally, by acquiring the minimum axial dynamic and static clearance values and the design limit value of the axial dynamic and static clearance before and after each stage of moving blade of the key component of the steam turbine under the target working condition, it can be judged whether structural optimization is required to be performed on the key component of the steam turbine, that is, whether design monitoring data of the key component meets the monitoring qualification condition or not.
Optionally, based on design monitoring data of the key component, whether the minimum value of the axial dynamic and static gaps before and after each stage of moving blade of the key component meets the monitoring qualification condition can be judged. If the design monitoring data does not meet the corresponding monitoring qualification conditions, determining that the key components of the steam turbine need to be subjected to structural optimization, and further carrying out structural optimization on the key components of the steam turbine.
According to the design monitoring method for the axial dynamic and static impact grinding safety of the flexibly-operated steam turbine, design monitoring is conducted on the steam turbine, design monitoring data of minimum axial dynamic and static clearance before and after each stage of moving blades of a key part of the steam turbine under a target working condition are obtained, structural design optimization improvement is conducted on the key part of the steam turbine when the design monitoring data of minimum axial dynamic and static clearance before and after each stage of moving blades under the target working condition do not meet the monitoring qualification condition, the axial dynamic and static impact grinding safety of the moving blades of the key part of the flexibly-operated steam turbine under the target working condition is in a controlled state, and long service life and high flexibility of the design of the flexibly-operated steam turbine are guaranteed from the aspect of the minimum axial dynamic and static clearance before and after each stage of moving blades.
Fig. 4 is a schematic flow chart of a design monitoring method for axial dynamic and static impact grinding safety of a flexibly operated steam turbine according to an embodiment of the disclosure, as shown in fig. 4, the method includes the following steps:
s401, obtaining the minimum axial dynamic and static clearance before and after each stage of moving blade of a key part of the steam turbine under a target working condition.
In embodiments of the present disclosure, key components of a steam turbine include a high pressure cylinder and a medium pressure cylinder. Obtaining minimum value delta y of axial dynamic clearance before each stage of moving blade of key component fjx Minimum value delta y of axial dynamic and static clearance behind moving blade bjx Wherein deltay represents the minimum axial dynamic and static clearance before and after each stage of moving blade, the subscript f represents before moving blade, the subscript b represents after moving blade, and the subscript j represents the working environment of key componentsH denotes high pressure, I denotes medium pressure, and x denotes the stage number of the rotor blade.
Alternatively, the minimum value deltay of the axial dynamic clearance before each stage of moving blade of the high-pressure cylinder under the target working condition of the steam turbine can be obtained based on the life monitoring module 21 in the device 200 fHx And the minimum value delta y of axial dynamic and static clearance after each stage of moving blade of high-pressure cylinder bHx For high pressure cylinder stage rotor blades, x=1, 2, ·, n, where n is the number of stages of the high-pressure cylinder moving blade.
Optionally, acquiring an axial dynamic clearance minimum value deltay before each stage of moving blade of the medium pressure cylinder of the steam turbine under the target working condition fIx And the minimum value delta y of axial dynamic and static clearance after each stage of moving blade of medium pressure cylinder bIx For a medium pressure cylinder moving blade, x=1, 2, ·, m, where m is the number of stages of the moving blade of the medium pressure cylinder.
S402, obtaining the design limit value of the axial dynamic and static clearance of the moving blade of the key part of the steam turbine.
Optionally, the dynamic and static clearance design limit value Y of the moving blade of the key component of the steam turbine under the target working condition is obtained j The symbol j indicates the critical component operating environment, H indicates high voltage, and I indicates medium voltage.
Optionally, the axial dynamic and static clearance design limit value Y before and after each stage of moving blade of the high-pressure cylinder under the target working condition of the steam turbine H 。
Optionally, the axial dynamic and static clearance design limit value Y of the turbine before and after each stage of moving blade of the intermediate pressure cylinder under the target working condition I 。
S403, determining the minimum value ratio of the axial dynamic and static gaps before and after each stage of moving blade of a key component of the steam turbine under the target working condition.
In embodiments of the present disclosure, R yfjx The ratio of the minimum value of the axial dynamic clearance before each stage of moving blade of the key component under the target working condition is represented by R ybjx Representing the ratio of the minimum value of the axial dynamic and static gaps behind the moving blade of the key part under the target working condition, R y The ratio of the minimum value of the axial dynamic and static gaps before and after each stage of moving blade is expressed, and the subscript f represents the moving bladeBefore, after the rotor blade is denoted by the subscript b, the subscript j denotes the working environment of the key component, H denotes the high pressure, I denotes the medium pressure, and x denotes the stage number of the rotor blade.
Optionally, a calculation formula of a first axial dynamic and static clearance ratio before each stage of moving blade of the high-pressure cylinder under a target working condition of the steam turbine is as followsThe calculation formula of the second axial dynamic and static clearance ratio behind each stage of moving blade of the high-pressure cylinder under the target working condition of the steam turbine is +.>
Optionally, a calculation formula of the third axial dynamic and static clearance ratio before each stage of moving blade of the intermediate pressure cylinder under the target working condition of the steam turbine is as followsThe calculation formula of the fourth axial dynamic and static clearance ratio of the turbine after each stage of moving blade of the medium pressure cylinder under the target working condition is +.>
S404, judging whether the minimum value of the axial clearance between the front moving blade and the rear moving blade of each stage of the key component meets the monitoring qualification condition.
In the embodiment of the disclosure, whether the minimum value of the axial clearance before and after each stage of moving blade of the key component meets the monitoring qualification condition is judged, that is, whether the design monitoring data meets the monitoring qualification condition is judged. The key components may be divided into a high pressure cylinder and a medium pressure cylinder. The minimum axial clearance of each stage of moving blade of the high-pressure cylinder comprises the minimum axial dynamic and static clearance before each stage of moving blade of the high-pressure cylinder and the minimum axial dynamic and static clearance after each stage of moving blade of the high-pressure cylinder. The axial clearance of each stage of moving blade of the medium pressure cylinder comprises a minimum value of the axial dynamic and static clearance before each stage of moving blade of the medium pressure cylinder and a minimum value of the axial dynamic and static clearance after each stage of moving blade of the medium pressure cylinder.
The design monitoring data comprise a first axial dynamic and static clearance ratio before each stage of moving blade of the high-pressure cylinder and a second axial dynamic and static clearance ratio after each stage of moving blade of the high-pressure cylinder, and if the first axial dynamic and static clearance ratio and the second axial dynamic and static clearance ratio are both larger than a third set threshold value, the minimum axial dynamic and static clearance designs before each stage of moving blade of the high-pressure cylinder and after the moving blade under the target working condition are determined to meet the monitoring qualification conditions, otherwise, the monitoring data of the design of each stage of moving blade of the high-pressure cylinder are determined to be abnormal design monitoring data.
The design monitoring data comprise a third axial dynamic and static clearance ratio before each stage of moving blade of the medium pressure cylinder and a fourth axial dynamic and static clearance ratio after each stage of moving blade of the medium pressure cylinder, and if the third axial dynamic and static clearance ratio and the fourth axial dynamic and static clearance ratio are both larger than a third set threshold value, the minimum axial dynamic and static clearance design before each stage of moving blade of the medium pressure cylinder and after the moving blade of the medium pressure cylinder under the target working condition is determined to meet the monitoring qualification condition, otherwise, the monitoring qualification condition is not met, and the design monitoring data of each stage of moving blade of the medium pressure cylinder is determined to be abnormal design monitoring data.
That is, the minimum design of the axial dynamic and static clearance before each stage of moving blade of the high-pressure cylinder of the steam turbine meets the condition of qualified monitoring
Optionally, the minimum value design of the axial dynamic clearance behind each stage of moving blade of the high-pressure cylinder of the steam turbine meets the condition of qualified monitoring
Optionally, the minimum design of the axial dynamic and static clearance before each stage of moving blade in the pressure cylinder in the steam turbine meets the condition of qualified monitoring
Alternatively, each stage of the pressure cylinder in the steam turbine movesThe minimum value design of the axial dynamic and static clearance behind the blade meets the monitoring qualification condition as follows
Optionally, the minimum design of the axial dynamic and static clearance before each stage of moving blade of the high-pressure cylinder of the steam turbine does not meet the condition of qualified monitoring
Optionally, the minimum value design of the axial dynamic clearance after each stage of moving blade of the high-pressure cylinder of the steam turbine does not meet the condition of qualified monitoring
Optionally, the minimum value design of the axial dynamic clearance before each stage of moving blade of the pressure cylinder in the steam turbine does not meet the condition of qualified monitoring
Optionally, the minimum value design of the axial dynamic clearance after each stage of moving blade of the pressure cylinder in the steam turbine does not meet the condition of qualified monitoring
S405, responding to the condition that the minimum value design monitoring of the axial dynamic and static gaps before and after each stage of moving blades of the turbine key component does not meet the monitoring qualification, and generating a structural optimization strategy set of the turbine key component.
Optionally, for a reaction turbine, turning the axial dimensions of the vane intermediate and the steam outlet side of the vane shroud and/or turning the axial dimensions of the vane intermediate and the steam inlet side of the vane shroud; for impulse turbines, the axial dimensions of the outer ring of the diaphragm and the steam outlet side of the diaphragm body are turned and/or the axial dimensions of the outer ring of the diaphragm and the steam inlet side of the diaphragm body are turned.
Alternatively, for the first stage of moving blade of each stage of high-pressure cylinderThe ratio of the axial dynamic clearance to the static clearance does not meet the monitoring qualification condition, and the generated optimization and improvement measure is the axial dimension of the steam outlet side of the stator blade shroud ring and the stator blade intermediate of the same-stage turning of the reaction turbine, or the axial dimension of the steam outlet side of the baffle plate outer ring and the baffle plate body of the same-stage turning of the impulse turbine, and the turning axial dimension y fH Is y fH ＝[Y H -Δy fHx +1]。
Wherein Y is H Design limit value delta y for axial dynamic and static clearance before and after each stage of moving blade of high-pressure cylinder of steam turbine fHx The axial dynamic and static clearance [ X ] is the front axial dynamic and static clearance of each stage of moving blade of a high-pressure cylinder of a steam turbine under the target working condition]The number X is expressed as an integer.
Optionally, for the second axial dynamic and static clearance ratio after each stage of moving blade of the high-pressure cylinder not meeting the monitoring qualification condition, the generated optimization and improvement measure is the axial dimension of the steam inlet side of the stator blade shroud and the stator blade intermediate of the next stage of turning of the reaction turbine, or the axial dimension of the steam inlet side of the baffle plate outer ring and the baffle plate body of the next stage of turning of the impulse turbine, and the turning axial dimension y bH Is y bH ＝[Y H -Δy bHx +1]。
Wherein Y is H Design limit value delta y for axial dynamic and static clearance before and after each stage of moving blade of high-pressure cylinder of steam turbine bHx The axial dynamic and static clearance is the minimum value of the axial dynamic and static clearance behind each stage of moving blade of the high-pressure cylinder under the target working condition.
Optionally, for the condition that the ratio of the third axial dynamic clearance to the static clearance before each stage of moving blade of the medium pressure cylinder does not meet the monitoring qualification, the generated optimization and improvement measure is the axial dimension of the steam outlet side of the stator blade shroud and the stator blade intermediate of the same stage of turning of the reaction turbine, or the axial dimension of the steam outlet side of the baffle plate outer ring and the baffle plate body of the same stage of turning of the impulse turbine, and the axial dimension y of the turning fI Is y fI ＝[Y I -Δy fIx +1]。
Wherein Y is I Design limit value delta y for axial dynamic and static clearance before and after each stage of moving blade of turbine medium pressure cylinder fIx For the middle of the turbine under the target working conditionAxial dynamic and static clearance minimum before each stage of moving blade of the pressure cylinder.
Optionally, for the fourth axial dynamic and static clearance ratio after each stage of moving blade of the medium pressure cylinder not meeting the monitoring qualification condition, the generated optimization and improvement measure is the axial dimension of the steam inlet side of the stator blade intermediate and the stator blade shroud of the next stage of turning of the reaction turbine, or the axial dimension of the steam inlet side of the baffle plate outer ring and the baffle plate body of the next stage of turning of the impulse turbine, and the turning axial dimension y bI Is y bI ＝[Y I -Δy bIx +1]。
Wherein Y is I Design limit value delta y for axial dynamic and static clearance before and after each stage of moving blade of turbine medium pressure cylinder bIx The minimum axial dynamic and static clearance behind each stage of moving blade of the medium pressure cylinder of the steam turbine under the target working condition.
According to the design monitoring method for the axial dynamic and static impact grinding safety of the flexibly-operated steam turbine, design monitoring is conducted on the steam turbine, design monitoring data of minimum axial dynamic and static clearance before and after each stage of moving blades of a key part of the steam turbine under a target working condition are obtained, structural design optimization improvement is conducted on the key part of the steam turbine when the design monitoring data of minimum axial dynamic and static clearance before and after each stage of moving blades under the target working condition do not meet the monitoring qualification condition, the axial dynamic and static impact grinding safety of the moving blades of the key part of the flexibly-operated steam turbine under the target working condition is in a controlled state, and long service life and high flexibility of the design of the flexibly-operated steam turbine are guaranteed from the aspect of the minimum axial dynamic and static clearance before and after each stage of moving blades.
The exemplary illustration is based on a model of ultra supercritical 1050MW single reheat turbine, impulse turbine, high pressure cylinder with 8 stages of moving blades, and medium pressure cylinder with 6 stages of moving blades.
The axial dynamic and static clearance minimum value deltay of the 1050MW steam turbine before each stage of moving blade of the high-pressure cylinder is originally designed and improved under the target working condition fHx And a first axial dynamic-static gap ratio R yfHx The results of the calculation of (2) are shown in Table 1, and the axial dynamic and static intervals before each stage of moving blade of the high-pressure cylinder of the steam turbineGap design threshold Y H Optimized and improved turning axial dimension y of outer ring of same-stage partition plate and steam outlet side of partition plate body fH The results of the calculation of (2) are also shown in Table 1.
The original design of the minimum value of the axial dynamic and static gaps before each stage of moving blade of the high-pressure cylinder of the 1050MW steam turbine under the target working condition does not meet the monitoring qualification condition, and y is given according to the table 1 fH The minimum value design of the axial dynamic and static clearance before each stage of moving blade of the high-pressure cylinder under the target working condition after the axial dimension of the outer ring of the same-stage baffle and the outlet steam side of the baffle body are turned meets the monitoring qualification condition.
Table 1 1050MW turbine is under the target working condition high pressure cylinder each stage moving vane front axial dynamic and static clearance design monitoring result
Axial dynamic and static clearance minimum value deltay of the turbine with 1050MW after each stage of moving blade of the high-pressure cylinder is designed and improved under target working condition bHx And a second axial dynamic-static gap ratio R ybHx The calculation results of (2) are shown in Table 2, and the design limit value Y of the axial dynamic and static clearance after each stage of moving blade of the high-pressure cylinder of the steam turbine H Optimized and improved turning axial dimension y of outer ring of next-stage partition plate and steam inlet side of partition plate body bH The results of the calculation of (2) are also shown in Table 2.
In the target working condition, in 8-stage moving blades of a high-pressure cylinder, the minimum value of axial dynamic and static clearances after the moving blades of the 5 th stage, the 6 th stage and the 7 th stage are originally designed does not meet the monitoring qualification condition, and y is given according to the table 2 fH The minimum value design of the axial dynamic and static clearance after turning the outer ring of the next-stage baffle and the steam inlet side axial dimension of the baffle body and each stage of moving blade of the high-pressure cylinder under the target working condition after improvement meets the monitoring qualification condition.
Table 2 shows the results of axial dynamic and static clearance design monitoring after each stage of moving blade of high pressure cylinder for 1050MW steam turbine under target working condition
The initial design and the improved front axial dynamic and static clearance minimum value deltay of each stage of moving blade of the intermediate pressure cylinder of the 1050MW steam turbine under the target working condition fIx And a third axial dynamic-static gap ratio R yfIx The calculation results of (2) are shown in Table 3, and the design limit value Y of the axial dynamic and static clearance before each stage of moving blade of the pressure cylinder in the steam turbine I Optimized and improved turning axial dimension y of outer ring of same-stage partition plate and steam outlet side of partition plate body fH The results of the calculation of (2) are also shown in Table 3.
In the target working condition of the 1050MW steam turbine, in the 6-stage moving blades of the medium pressure cylinder, the minimum value of the axial dynamic and static clearance before the 2 nd-6 th-stage moving blades are originally designed does not meet the monitoring qualification condition, and y is given according to the table 3 fI The minimum value design of the axial dynamic and static clearance before each stage of moving blade of the medium pressure cylinder under the target working condition after the axial dimension of the outer ring of the same-stage baffle and the outlet steam side of the baffle body are turned meets the monitoring qualification condition.
Table 3 design monitoring result of axial dynamic and static clearance before each stage of moving blade of intermediate pressure cylinder for 1050MW steam turbine under target working condition
Axial dynamic and static clearance minimum value deltay of the turbine with 1050MW after each stage of moving blade of the intermediate pressure cylinder is designed and improved under target working condition bIx And a fourth axial dynamic-static gap ratio R ybIx The calculation results of (2) are shown in Table 4, and the design limit value Y of the axial dynamic and static clearance after each stage of moving blade in the pressure cylinder in the steam turbine I Optimized and improved turning axial dimension y of outer ring of next-stage partition plate and steam outlet side of partition plate body bI The results of the calculation of (2) are also shown in Table 4.
In the target working condition of the 1050MW steam turbine, in the 6-stage moving blades of the medium pressure cylinder, the minimum value of the axial dynamic and static clearance after the 4 th-6 th-stage moving blades are originally designed does not meet the monitoring qualification condition, and y is given according to the table 4 bI Axial dimension and improvement of steam inlet side of outer ring and baffle body of baffle plate at next stage of turningAnd then, the minimum value design of the axial dynamic and static clearance behind each stage of moving blade of the medium pressure cylinder under the target working condition meets the monitoring qualification condition.
Table 4 shows the design monitoring results of axial dynamic and static clearance after each stage of moving blade of intermediate pressure cylinder for 1050MW steam turbine under target working condition
In order to achieve the above embodiment, the present disclosure further provides a safety design monitoring device for flexibly operating axial dynamic and static impact grinding of a steam turbine.
Fig. 5 is a schematic structural diagram of a design monitoring device for axial dynamic and static impact grinding safety of a flexibly operated steam turbine according to an embodiment of the present disclosure.
As shown in fig. 5, the flexible operation turbine axial dynamic and static impact grinding safety design monitoring device 500 includes:
the first obtaining module 501 is configured to obtain axial dynamic and static clearance monitoring data of each stage of moving blade of a key component of the steam turbine under a target working condition.
And the second obtaining module 502 is configured to obtain an axial dynamic and static clearance design limit value of each stage of moving blade of the key component.
A determining module 503, configured to determine design monitoring data of the key component based on the axial dynamic and static clearance monitoring data and the axial dynamic and static clearance design threshold value for each stage of moving blade.
And the optimization module 504 is used for performing structural optimization on key components of the steam turbine based on the design monitoring data.
In a possible implementation manner of the embodiment of the present disclosure, the determining module 503 is further configured to: based on the axial dynamic and static clearance monitoring data, determining a first axial dynamic and static clearance minimum value before the moving blade and a second axial dynamic and static clearance minimum value after the moving blade; acquiring the ratio of the minimum value of the first axial dynamic and static clearance before the moving blade to the design limit value of the axial dynamic and static clearance as the axial dynamic and static clearance ratio before the moving blade; acquiring the ratio of the minimum value of the second axial dynamic and static clearance after the moving blade to the design limit value of the axial dynamic and static clearance as the axial dynamic and static clearance ratio after the moving blade; and determining the axial dynamic and static clearance ratio before the moving blade and the axial dynamic and static clearance ratio after the moving blade of each stage as design monitoring data of the key component.
In one possible implementation of the embodiment of the disclosure, the optimization module 504 is further configured to: for each stage of moving blade of the key component, judging whether the minimum value of the axial dynamic and static gaps before and after the moving blade meets the monitoring qualification condition based on the axial dynamic and static gap ratio before the moving blade and the axial dynamic and static gap ratio before the moving blade; and if the minimum value of the axial dynamic and static gaps before and after the first-stage moving blade does not meet the corresponding monitoring qualification condition, carrying out structural optimization on the key components of the steam turbine.
In one possible implementation of the embodiment of the disclosure, the optimization module 504 is further configured to: the design monitoring data comprise a first axial dynamic and static clearance ratio before each stage of moving blades of the high-pressure cylinder and a second axial dynamic and static clearance ratio after each stage of moving blades of the high-pressure cylinder, and if the first axial dynamic and static clearance ratio and the second axial dynamic and static clearance ratio are both larger than a set threshold value, the minimum axial dynamic and static clearance design before and after each stage of moving blades of the high-pressure cylinder under a target working condition is determined to meet the monitoring qualification condition, otherwise, the minimum axial dynamic and static clearance design does not meet the monitoring qualification condition; the design monitoring data comprise a third axial dynamic and static clearance ratio before each stage of moving blade of the medium pressure cylinder and a fourth axial dynamic and static clearance ratio after each stage of moving blade of the medium pressure cylinder, and if the third axial dynamic and static clearance ratio and the fourth axial dynamic and static clearance ratio are both larger than a set threshold value, the minimum axial dynamic and static clearance design before each stage of moving blade and after the moving blade of the medium pressure cylinder under a target working condition is determined to meet the monitoring qualification condition, otherwise, the minimum axial dynamic and static clearance design after each stage of moving blade of the medium pressure cylinder is determined to not meet the monitoring qualification condition.
In one possible implementation of the embodiment of the disclosure, the optimization module 504 is further configured to: determining design monitoring data of key components of the moving blade which do not meet the monitoring qualification condition, and taking the design monitoring data as abnormal monitoring data; generating a structural optimization strategy set of the steam turbine based on the anomaly monitoring data, wherein the structural optimization strategy set comprises at least one structural optimization improvement strategy; and carrying out structural optimization on the steam turbine according to the structural optimization strategy set, and continuously collecting the design monitoring data and subsequent operation until the design monitoring data of the moving blades of each stage meet the monitoring qualification condition, and stopping structural optimization.
In one possible implementation of the embodiment of the disclosure, the optimization module 504 is further configured to: after the abnormal design monitoring data are determined, generating abnormal prompt information according to the abnormal design monitoring data, target key components to which the abnormal design monitoring data belong and corresponding target monitoring dimensions; and acquiring contact information of a feedback object, and sending the abnormal prompt information to the feedback object according to the contact information.
In one possible implementation of the embodiment of the disclosure, the optimization module 504 is further configured to: determining a design anomaly type of the moving blade of the critical component based on the anomaly design monitoring data; and determining the structure optimization strategy set according to the type of the steam turbine and the design abnormality type of the moving blades.
In one possible implementation of the embodiments of the present disclosure, the set of structural optimization policies includes one or more of the following policies: turning the axial dimension of the steam outlet side of the stator blade intermediate and the stator blade shroud and/or turning the axial dimension of the steam inlet side of the stator blade intermediate and the stator blade shroud; turning the axial dimension of the outer ring of the baffle plate and the steam outlet side of the baffle plate body and/or turning the axial dimension of the outer ring of the baffle plate and the steam inlet side of the baffle plate body; turning the axial dimension of the steam outlet side of the stator blade shroud and the stator blade intermediate of the same stage; turning the axial dimensions of the outer ring of the same-stage partition plate and the steam outlet side of the partition plate body; turning the axial dimensions of the inlet side of the stator blade shroud and the stator blade intermediate of the next stage; turning the axial dimension of the outer ring of the baffle plate at the next stage and the steam inlet side of the baffle plate body.
In one possible implementation of the disclosed embodiments, the target operating condition is a fast start-up and/or fast load-varying hill climbing transient operating condition of the steam turbine.
In the design monitoring device for the axial dynamic and static impact grinding safety of the flexibly-operated steam turbine, design monitoring is carried out on the steam turbine to obtain minimum design monitoring data of axial dynamic and static gaps before and after each stage of moving blades of a key part of the steam turbine under a target working condition, and structural design optimization improvement is carried out on the key part of the steam turbine when the minimum design monitoring data of the axial dynamic and static gaps before and after each stage of moving blades under the target working condition does not meet the monitoring qualification condition, so that the axial dynamic and static impact grinding safety of the moving blades of the key part of the flexibly-operated steam turbine under the target working condition is in a controlled state, and long service life and high flexibility of the design of the flexibly-operated steam turbine are ensured from the aspect of the minimum design of the axial dynamic and static gaps before and after each stage of moving blades.
It should be noted that, the foregoing explanation of the embodiment of the method for monitoring the axial dynamic and static impact grinding safety design of the flexibly operating steam turbine is also applicable to the device for monitoring the axial dynamic and static impact grinding safety design of the flexibly operating steam turbine of this embodiment, and will not be repeated here.
In order to achieve the above embodiments, the present disclosure further proposes an electronic device including: a processor, and a memory communicatively coupled to the processor; the memory stores computer-executable instructions; the processor executes the computer-executable instructions stored in the memory to implement the methods provided by the previous embodiments.
In order to implement the above-described embodiments, the present disclosure also proposes a computer-readable storage medium having stored therein computer-executable instructions that, when executed by a processor, are adapted to implement the methods provided by the foregoing embodiments.
To achieve the above embodiments, the present disclosure also proposes a computer program product comprising a computer program which, when executed by a processor, implements the method provided by the foregoing embodiments.
The processes of collecting, storing, using, processing, transmitting, providing, disclosing and the like of the personal information of the user involved in the present disclosure all conform to the regulations of the relevant laws and regulations and do not violate the public order colloquial.
It should be noted that personal information from users should be collected for legitimate and reasonable uses and not shared or sold outside of these legitimate uses. In addition, such collection/sharing should be performed after receiving user informed consent, including but not limited to informing the user to read user agreements/user notifications and signing agreements/authorizations including authorization-related user information before the user uses the functionality. In addition, any necessary steps are taken to safeguard and ensure access to such personal information data and to ensure that other persons having access to the personal information data adhere to their privacy policies and procedures.
The present disclosure contemplates embodiments that may provide a user with selective prevention of use or access to personal information data. That is, the present disclosure contemplates that hardware and/or software may be provided to prevent or block access to such personal information data. Once personal information data is no longer needed, risk can be minimized by limiting data collection and deleting data. In addition, personal identification is removed from such personal information, as applicable, to protect the privacy of the user.
In the foregoing descriptions of embodiments, descriptions of the terms "one embodiment," "some embodiments," "examples," "particular examples," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the disclosure. In this specification, schematic representations of the above terms are not necessarily directed to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, the different embodiments or examples described in this specification and the features of the different embodiments or examples may be combined and combined by those skilled in the art without contradiction.
Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In the description of the present disclosure, the meaning of "a plurality" is at least two, such as two, three, etc., unless explicitly specified otherwise.
Any process or method descriptions in flow charts or otherwise described herein may be understood as representing modules, segments, or portions of code which include one or more executable instructions for implementing specific logical functions or steps of the process, and additional implementations are included within the scope of the preferred embodiment of the present disclosure in which functions may be executed out of order from that shown or discussed, including substantially concurrently or in reverse order, depending on the functionality involved, as would be understood by those reasonably skilled in the art of the embodiments of the present disclosure.
Logic and/or steps represented in the flowcharts or otherwise described herein, e.g., a ordered listing of executable instructions for implementing logical functions, can be embodied in any computer-readable medium for use by or in connection with an instruction execution system, apparatus, or device, such as a computer-based system, processor-containing system, or other system that can fetch the instructions from the instruction execution system, apparatus, or device and execute the instructions. For the purposes of this description, a "computer-readable medium" can be any means that can contain, store, communicate, propagate, or transport the program for use by or in connection with the instruction execution system, apparatus, or device. More specific examples (a non-exhaustive list) of the computer-readable medium would include the following: an electrical connection (electronic device) having one or more wires, a portable computer diskette (magnetic device), a Random Access Memory (RAM), a read-only memory (ROM), an erasable programmable read-only memory (EPROM or flash memory), an optical fiber device, and a portable compact disc read-only memory (CDROM). In addition, the computer readable medium may even be paper or other suitable medium on which the program is printed, as the program may be electronically captured, via, for instance, optical scanning of the paper or other medium, then compiled, interpreted or otherwise processed in a suitable manner, if necessary, and then stored in a computer memory.
It should be understood that portions of the present disclosure may be implemented in hardware, software, firmware, or a combination thereof. In the above-described embodiments, the various steps or methods may be implemented in software or firmware stored in a memory and executed by a suitable instruction execution system. As with the other embodiments, if implemented in hardware, may be implemented using any one or combination of the following techniques, as is well known in the art: discrete logic circuits having logic gates for implementing logic functions on data signals, application specific integrated circuits having suitable combinational logic gates, programmable Gate Arrays (PGAs), field Programmable Gate Arrays (FPGAs), and the like.
Those of ordinary skill in the art will appreciate that all or a portion of the steps carried out in the method of the above-described embodiments may be implemented by a program to instruct related hardware, where the program may be stored in a computer readable storage medium, and where the program, when executed, includes one or a combination of the steps of the method embodiments.
Furthermore, each functional unit in the embodiments of the present disclosure may be integrated in one processing module, or each unit may exist alone physically, or two or more units may be integrated in one module. The integrated modules may be implemented in hardware or in software functional modules. The integrated modules may also be stored in a computer readable storage medium if implemented in the form of software functional modules and sold or used as a stand-alone product.
The above-mentioned storage medium may be a read-only memory, a magnetic disk or an optical disk, or the like. Although embodiments of the present disclosure have been shown and described above, it will be understood that the above embodiments are illustrative and not to be construed as limiting the present disclosure, and that variations, modifications, alternatives, and variations may be made to the above embodiments by one of ordinary skill in the art within the scope of the present disclosure.
Claims (21)
1. The design monitoring method for the axial dynamic and static impact grinding safety of the flexibly-operated steam turbine is characterized by comprising the following steps of:
acquiring axial dynamic and static clearance monitoring data of each stage of moving blades of a key component of the steam turbine under a target working condition;
acquiring an axial dynamic and static clearance design limit value of each stage of moving blade of the key component;
determining design monitoring data of the key component according to the axial dynamic and static clearance monitoring data and the axial dynamic and static clearance design limit value aiming at each stage of moving blades;
and carrying out structural optimization on key components of the steam turbine based on the design monitoring data.
2. The method of claim 1, wherein the determining design monitoring data for the critical component based on the axial dynamic clearance monitoring data and the axial dynamic clearance design limit comprises:
Based on the axial dynamic and static clearance monitoring data, determining a first axial dynamic and static clearance minimum value before the moving blade and a second axial dynamic and static clearance minimum value after the moving blade;
acquiring the ratio of the minimum value of the first axial dynamic and static clearance before the moving blade to the design limit value of the axial dynamic and static clearance as the axial dynamic and static clearance ratio before the moving blade;
acquiring the ratio of the minimum value of the second axial dynamic and static clearance after the moving blade to the design limit value of the axial dynamic and static clearance as the axial dynamic and static clearance ratio after the moving blade;
and determining the axial dynamic and static clearance ratio before the moving blade and the axial dynamic and static clearance ratio after the moving blade of each stage as design monitoring data of the key component.
3. The method of claim 1, wherein the structurally optimizing critical components of the steam turbine based on the design monitoring data comprises:
for each stage of moving blade of the key component, judging whether the minimum value of the axial dynamic and static gaps before and after the moving blade meets the monitoring qualification condition based on the axial dynamic and static gap ratio before the moving blade and the axial dynamic and static gap ratio before the moving blade;
And if the minimum value of the axial dynamic and static gaps before and after the first-stage moving blade does not meet the corresponding monitoring qualification condition, carrying out structural optimization on the key components of the steam turbine.
4. A method according to claim 3, characterized in that the method further comprises:
the design monitoring data comprise a first axial dynamic and static clearance ratio before each stage of moving blades of the high-pressure cylinder and a second axial dynamic and static clearance ratio after each stage of moving blades of the high-pressure cylinder, and if the first axial dynamic and static clearance ratio and the second axial dynamic and static clearance ratio are both larger than a set threshold value, the minimum axial dynamic and static clearance design before and after each stage of moving blades of the high-pressure cylinder under a target working condition is determined to meet the monitoring qualification condition, otherwise, the minimum axial dynamic and static clearance design does not meet the monitoring qualification condition;
the design monitoring data comprise a third axial dynamic and static clearance ratio before each stage of moving blade of the medium pressure cylinder and a fourth axial dynamic and static clearance ratio after each stage of moving blade of the medium pressure cylinder, and if the third axial dynamic and static clearance ratio and the fourth axial dynamic and static clearance ratio are both larger than a set threshold value, the minimum axial dynamic and static clearance design before each stage of moving blade and after the moving blade of the medium pressure cylinder under a target working condition is determined to meet the monitoring qualification condition, otherwise, the minimum axial dynamic and static clearance design after each stage of moving blade of the medium pressure cylinder is determined to not meet the monitoring qualification condition.
5. The method of any of claims 1-4, wherein the structurally optimizing critical components of the steam turbine based on the design monitoring data comprises:
determining design monitoring data of key components of the moving blade which do not meet the monitoring qualification condition, and taking the design monitoring data as abnormal monitoring data;
generating a structural optimization strategy set of the steam turbine based on the anomaly monitoring data, wherein the structural optimization strategy set comprises at least one structural optimization improvement strategy;
and carrying out structural optimization on the steam turbine according to the structural optimization strategy set, and continuously collecting the design monitoring data and subsequent operation until the design monitoring data of the moving blades of each stage meet the monitoring qualification condition, and stopping structural optimization.
6. The method of claim 5, wherein the method further comprises:
after the abnormal design monitoring data are determined, generating abnormal prompt information according to the abnormal design monitoring data, target key components to which the abnormal design monitoring data belong and corresponding target monitoring dimensions;
and acquiring contact information of a feedback object, and sending the abnormal prompt information to the feedback object according to the contact information.
7. The method of claim 5, wherein generating the set of structural optimization strategies for the steam turbine comprises:
determining a design anomaly type of the moving blade of the critical component based on the anomaly design monitoring data;
and determining the structure optimization strategy set according to the type of the steam turbine and the design abnormality type of the moving blades.
8. The method of claim 7, wherein the set of structural optimization policies includes one or more of the following policies:
turning the axial dimension of the steam outlet side of the stator blade intermediate and the stator blade shroud and/or turning the axial dimension of the steam inlet side of the stator blade intermediate and the stator blade shroud;
turning the axial dimension of the outer ring of the baffle plate and the steam outlet side of the baffle plate body and/or turning the axial dimension of the outer ring of the baffle plate and the steam inlet side of the baffle plate body;
turning the axial dimension of the steam outlet side of the stator blade shroud and the stator blade intermediate of the same stage;
turning the axial dimensions of the outer ring of the same-stage partition plate and the steam outlet side of the partition plate body;
turning the axial dimensions of the inlet side of the stator blade shroud and the stator blade intermediate of the next stage;
turning the axial dimension of the outer ring of the baffle plate at the next stage and the steam inlet side of the baffle plate body.
9. The method of claim 1, wherein the target operating condition is a rapid start-up and/or a rapid load change hill climbing transient operating condition of a steam turbine.
10. The utility model provides a flexible operation steam turbine axial moves quiet bump grinding security design monitoring device which characterized in that includes:
the first acquisition module is used for acquiring axial dynamic and static clearance monitoring data of each stage of moving blades of the key component of the steam turbine under the target working condition;
the second acquisition module is used for acquiring an axial dynamic and static clearance design limit value of each stage of moving blades of the key component;
the determining module is used for determining design monitoring data of the key component according to the axial dynamic and static clearance monitoring data and the axial dynamic and static clearance design limit value aiming at each stage of moving blades;
and the optimization module is used for carrying out structural optimization on the key components of the steam turbine based on the design monitoring data.
11. The apparatus of claim 10, wherein the determining module is further configured to:
based on the axial dynamic and static clearance monitoring data, determining a first axial dynamic and static clearance minimum value before the moving blade and a second axial dynamic and static clearance minimum value after the moving blade;
Acquiring the ratio of the minimum value of the first axial dynamic and static clearance before the moving blade to the design limit value of the axial dynamic and static clearance as the axial dynamic and static clearance ratio before the moving blade;
acquiring the ratio of the minimum value of the second axial dynamic and static clearance after the moving blade to the design limit value of the axial dynamic and static clearance as the axial dynamic and static clearance ratio after the moving blade;
and determining the axial dynamic and static clearance ratio before the moving blade and the axial dynamic and static clearance ratio after the moving blade of each stage as design monitoring data of the key component.
12. The apparatus of claim 10, wherein the optimization module is further configured to:
for each stage of moving blade of the key component, judging whether the minimum value of the axial dynamic and static gaps before and after the moving blade meets the monitoring qualification condition based on the axial dynamic and static gap ratio before the moving blade and the axial dynamic and static gap ratio before the moving blade;
and if the minimum value of the axial dynamic and static gaps before and after the first-stage moving blade does not meet the corresponding monitoring qualification condition, carrying out structural optimization on the key components of the steam turbine.
13. The apparatus of claim 12, wherein the optimization module is further configured to:
The design monitoring data comprise a first axial dynamic and static clearance ratio before each stage of moving blades of the high-pressure cylinder and a second axial dynamic and static clearance ratio after each stage of moving blades of the high-pressure cylinder, and if the first axial dynamic and static clearance ratio and the second axial dynamic and static clearance ratio are both larger than a set threshold value, the minimum axial dynamic and static clearance design before and after each stage of moving blades of the high-pressure cylinder under a target working condition is determined to meet the monitoring qualification condition, otherwise, the minimum axial dynamic and static clearance design does not meet the monitoring qualification condition;
the design monitoring data comprise a third axial dynamic and static clearance ratio before each stage of moving blade of the medium pressure cylinder and a fourth axial dynamic and static clearance ratio after each stage of moving blade of the medium pressure cylinder, and if the third axial dynamic and static clearance ratio and the fourth axial dynamic and static clearance ratio are both larger than a set threshold value, the minimum axial dynamic and static clearance design before each stage of moving blade and after the moving blade of the medium pressure cylinder under a target working condition is determined to meet the monitoring qualification condition, otherwise, the minimum axial dynamic and static clearance design after each stage of moving blade of the medium pressure cylinder is determined to not meet the monitoring qualification condition.
14. The apparatus of any one of claims 10-13, wherein the optimization module is further configured to:
determining design monitoring data of key components of the moving blade which do not meet the monitoring qualification condition, and taking the design monitoring data as abnormal monitoring data;
Generating a structural optimization strategy set of the steam turbine based on the anomaly monitoring data, wherein the structural optimization strategy set comprises at least one structural optimization improvement strategy;
and carrying out structural optimization on the steam turbine according to the structural optimization strategy set, and continuously collecting the design monitoring data and subsequent operation until the design monitoring data of the moving blades of each stage meet the monitoring qualification condition, and stopping structural optimization.
15. The apparatus of claim 14, wherein the optimization module is further configured to:
after the abnormal design monitoring data are determined, generating abnormal prompt information according to the abnormal design monitoring data, target key components to which the abnormal design monitoring data belong and corresponding target monitoring dimensions;
and acquiring contact information of a feedback object, and sending the abnormal prompt information to the feedback object according to the contact information.
16. The apparatus of claim 14, wherein the optimization module is further configured to:
determining a design anomaly type of the moving blade of the critical component based on the anomaly design monitoring data;
and determining the structure optimization strategy set according to the type of the steam turbine and the design abnormality type of the moving blades.
17. The apparatus of claim 16, wherein the set of structural optimization policies comprises one or more of the following policies:
turning the axial dimension of the steam outlet side of the stator blade intermediate and the stator blade shroud and/or turning the axial dimension of the steam inlet side of the stator blade intermediate and the stator blade shroud;
turning the axial dimension of the outer ring of the baffle plate and the steam outlet side of the baffle plate body and/or turning the axial dimension of the outer ring of the baffle plate and the steam inlet side of the baffle plate body;
turning the axial dimension of the steam outlet side of the stator blade shroud and the stator blade intermediate of the same stage;
turning the axial dimensions of the outer ring of the same-stage partition plate and the steam outlet side of the partition plate body;
turning the axial dimensions of the inlet side of the stator blade shroud and the stator blade intermediate of the next stage;
turning the axial dimension of the outer ring of the baffle plate at the next stage and the steam inlet side of the baffle plate body.
18. The apparatus of claim 10, wherein the target operating condition is a rapid start-up and/or a rapid load change hill climbing transient operating condition of the steam turbine.
19. An electronic device, comprising:
a processor, and a memory communicatively coupled to the processor;
the memory stores computer-executable instructions;
The processor executes computer-executable instructions stored in the memory to implement the method of any one of claims 1-9.
20. A computer readable storage medium having stored therein computer executable instructions which when executed by a processor are adapted to carry out the method of any one of claims 1-9.
21. A computer program product comprising a computer program which, when executed by a processor, implements the method of any of claims 1-9.
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Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN203856517U (en) * | 2014-01-26 | 2014-10-01 | 国家电网公司 | Steam turbine internal cylinder capable of measuring dynamic and static clearance |
| CN106446329A (en) * | 2015-08-12 | 2017-02-22 | 通用电气公司 | Virtual turbomachine blade contact gap inspection |
| US20170343001A1 (en) * | 2016-05-26 | 2017-11-30 | Rolls-Royce Corporation | Impeller shroud with pneumatic piston for clearance control in a centrifugal compressor |
| US20200282965A1 (en) * | 2019-03-08 | 2020-09-10 | Donald Pieronek | Fault tolerant modualted trailer braking system |
| CN113250759A (en) * | 2021-04-30 | 2021-08-13 | 上海慕帆动力科技有限公司 | TRT clearance governing system |
| CN114412589A (en) * | 2021-12-01 | 2022-04-29 | 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 |
| CN115143919A (en) * | 2022-05-18 | 2022-10-04 | 三一(韶山)风电设备有限公司 | Method and device for detecting die assembly clearance of wind power blade |
| CN115450709A (en) * | 2022-08-16 | 2022-12-09 | 上海发电设备成套设计研究院有限责任公司 | Monitoring method and monitoring system device for turbine blade top clearance |
| US20230008935A1 (en) * | 2021-07-09 | 2023-01-12 | General Electric Company | Airfoil arrangement for a gas turbine engine utilizing a shape memory alloy |
| CN116361960A (en) * | 2023-06-01 | 2023-06-30 | 中国航发四川燃气涡轮研究院 | Method for designing radial clearance of gas turbine |
-
2023
- 2023-10-24 CN CN202311387835.2A patent/CN117669141A/en active Pending
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN203856517U (en) * | 2014-01-26 | 2014-10-01 | 国家电网公司 | Steam turbine internal cylinder capable of measuring dynamic and static clearance |
| CN106446329A (en) * | 2015-08-12 | 2017-02-22 | 通用电气公司 | Virtual turbomachine blade contact gap inspection |
| US20170343001A1 (en) * | 2016-05-26 | 2017-11-30 | Rolls-Royce Corporation | Impeller shroud with pneumatic piston for clearance control in a centrifugal compressor |
| US20200282965A1 (en) * | 2019-03-08 | 2020-09-10 | Donald Pieronek | Fault tolerant modualted trailer braking system |
| CN113250759A (en) * | 2021-04-30 | 2021-08-13 | 上海慕帆动力科技有限公司 | TRT clearance governing system |
| US20230008935A1 (en) * | 2021-07-09 | 2023-01-12 | General Electric Company | Airfoil arrangement for a gas turbine engine utilizing a shape memory alloy |
| CN114412589A (en) * | 2021-12-01 | 2022-04-29 | 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 |
| CN115143919A (en) * | 2022-05-18 | 2022-10-04 | 三一(韶山)风电设备有限公司 | Method and device for detecting die assembly clearance of wind power blade |
| CN115450709A (en) * | 2022-08-16 | 2022-12-09 | 上海发电设备成套设计研究院有限责任公司 | Monitoring method and monitoring system device for turbine blade top clearance |
| CN116361960A (en) * | 2023-06-01 | 2023-06-30 | 中国航发四川燃气涡轮研究院 | Method for designing radial clearance of gas turbine |
Non-Patent Citations (5)
| Title |
|---|
| MARCEL OETTINGER, ET AL.: "Loss Assessment of the Axial-Gap Size Effect in a Low-Pressure Turbine", 《JOURNALOFTHEGLOBALPOWERANDPROPULSIONSOCIETY》, 26 January 2021 (2021-01-26) * |
| 刘冠军: "东汽X300P型汽轮机轴向间隙计算及胀差大原因分析", 《华电技术》, 31 January 2019 (2019-01-31) * |
| 史进渊 等: "汽轮机零部件强度有限元分析的设计判据", 《热力透平》, vol. 40, no. 1, 31 March 2011 (2011-03-31), pages 22 - 27 * |
| 王宪磊 等: "叶片前缘前掠对离心压气机性能的影响", 《车用发动机》, 31 August 2023 (2023-08-31) * |
| 马国林，杨亚媛: "国产200MW机组动静间隙分布与振动限值的关系研究", 东北电力技术, no. 06, 30 June 1996 (1996-06-30) * |
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