CN113569441B - Pipeline vibration screening and monitoring point selecting method - Google Patents
Pipeline vibration screening and monitoring point selecting method Download PDFInfo
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- CN113569441B CN113569441B CN202110660083.7A CN202110660083A CN113569441B CN 113569441 B CN113569441 B CN 113569441B CN 202110660083 A CN202110660083 A CN 202110660083A CN 113569441 B CN113569441 B CN 113569441B
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- 238000000034 method Methods 0.000 title claims abstract description 24
- 238000012544 monitoring process Methods 0.000 title claims abstract description 23
- 238000012216 screening Methods 0.000 title claims description 14
- 238000013461 design Methods 0.000 claims abstract description 18
- 238000005457 optimization Methods 0.000 claims abstract description 8
- 239000008186 active pharmaceutical agent Substances 0.000 claims description 8
- 239000011159 matrix material Substances 0.000 claims description 7
- 238000005452 bending Methods 0.000 claims description 6
- 230000008878 coupling Effects 0.000 claims description 6
- 238000010168 coupling process Methods 0.000 claims description 6
- 238000005859 coupling reaction Methods 0.000 claims description 6
- 238000011156 evaluation Methods 0.000 claims description 4
- 238000006073 displacement reaction Methods 0.000 claims description 3
- 230000010349 pulsation Effects 0.000 claims description 3
- 238000005259 measurement Methods 0.000 abstract description 9
- 230000008569 process Effects 0.000 abstract description 4
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 238000007689 inspection Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
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Classifications
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
- G06F30/23—Design optimisation, verification or simulation using finite element methods [FEM] or finite difference methods [FDM]
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
- F17D—PIPE-LINE SYSTEMS; PIPE-LINES
- F17D5/00—Protection or supervision of installations
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2113/00—Details relating to the application field
- G06F2113/14—Pipes
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/04—Ageing analysis or optimisation against ageing
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- Monitoring And Testing Of Nuclear Reactors (AREA)
Abstract
Compared with the prior art, the method can be applied to vibration analysis and optimization in the design analysis of the nuclear power station pipeline, can also be used for guiding the vibration measurement and monitoring position of the pipeline, and is also applicable to the vibration analysis and measurement of process pipelines of other various power stations or workshops; the method can optimize the pipeline design, reduce vibration problems, improve pertinence of vibration measurement and monitoring and realize the purpose of the invention.
Description
Technical Field
The invention relates to a method for screening and monitoring point selection, in particular to a method for screening and monitoring point selection of pipeline vibration for power station pipeline vibration analysis and monitoring.
Background
The alternating stress generated by the vibration of the pipeline can cause fatigue damage, reduce the service life of the pipeline and even cause pipeline fracture failure, thereby endangering the operation safety of the nuclear power plant. With the occurrence of problems of vibration and noise of pipelines of newly-built and in-service nuclear power stations, the vibration and noise reduction design of the pipelines of the nuclear power stations is increasingly focused.
At present, vibration problems are not considered in design analysis of a nuclear power station pipeline, and the vibration problems are mainly treated by measuring and monitoring vibration before and during the service after the nuclear power station is built, and special treatment is performed after abnormal vibration is found, so that a great amount of time and expense are consumed for related analysis and transformation. Therefore, the method for screening the vibration of the pipeline and selecting the monitoring points is developed, the vibration probability and the fatigue severity of the pipeline are analyzed and evaluated in the design stage, and the method has important significance for optimizing the design, reducing the occurrence of vibration problems and improving the pertinence of vibration measurement and monitoring.
Currently, the most important nuclear power pipeline vibration control criterion is ASME OM (ASME Operation and Maintenance of Nuclear Power Power, hereinafter referred to as OM specification), which only gives a speed limit from the viewpoint of preventing vibration fatigue, is used for vibration inspection before and after the power station is built, does not give a method for reducing resonance possibility in the design stage, and does not give an accurate vibration speed measurement point.
The Westinghouse corporation in the United states sets screening criteria for AP1000 pile-type primary loop pipelines, and takes the coupling condition of the frequency of various potential vibration excitation sources, the natural frequency of the pipelines and the like into consideration, so that pipeline sections with high resonance possibility are screened. However, only the coupling between the first-order frequency and the vibration source is considered in the analysis, and the result is limited. If the frequency of each stage of pipeline within a certain range of potential vibration source frequency is considered, the number of the screened pipelines which are likely to vibrate is greatly increased, design optimization cannot be guided, and meanwhile, the fatigue severity caused by different vibrations cannot be reflected by the method.
The Institute of Energy Institute (London, EIs) writes guidelines for avoiding the vibration fatigue failure of process pipelines, and the EIs guidelines give out the possibility of the vibration failure of the pipeline system based on the characteristics of various vibrations and pipeline arrangement parameters, but the method has no practical modeling calculation, is difficult to estimate the resonance possibility, and cannot accurately consider the severity of the vibration fatigue of the pipelines.
Thus, there is a particular need for a method of screening and monitoring point selection for pipeline vibration that addresses the above-described existing problems.
Disclosure of Invention
The invention aims to provide a method for screening and selecting monitoring points of pipeline vibration, which aims at the defects of the prior art, has the characteristics of mature theory, no need of modeling analysis again, high analysis efficiency and easy practice, and can be widely applied to design optimization of various power station process pipeline systems.
The technical problems solved by the invention can be realized by adopting the following technical scheme:
a method of pipeline vibration screening and monitoring point selection comprising the steps of:
s1, calculating the speed and the stress of each node mode of a pipeline by taking a mode analysis result in pipeline design analysis, including the frequency of each mode, the mode displacement and the mode force of each node as inputs;
the modal velocity of node k is given by:
wherein χ is n，k Matrix form, ω representing nth order mode of k node n A circular frequency representing an nth order mode;
the formula of modal stress for node k:
wherein M is kx 、M ky Respectively representing bending moments in two directions of k node, W is section modulus of the pipeline, C 2 、K 2 Secondary stress and local stress coefficients in ASME BPVC fatigue calculation;
s2, taking a maximum stress node as a fatigue failure concern point, taking a maximum speed node as a vibration monitoring point, and calculating the ratio DS of the maximum modal stress and the maximum modal speed of the pipeline, wherein the DS value represents the magnitude of alternating bending moment stress under the same vibration speed and is used for reflecting the severity degree of fatigue caused by modal resonance of each stage;
s3, collecting and calculating potential vibration source frequencies, including pump frequency, impeller frequency, vortex shedding frequency, sound frequency and the like, wherein the pump frequency is determined according to the running rotation speed of the pump, and the impeller pressure pulsation frequency is equal to the main pump frequency multiplied by the number of blades of the impeller;
the vortex shedding frequency calculation formula of the stagnation pipe tee joint comprises the following steps:
wherein d represents the inner diameter of the branch pipe, r is the inner chamfer radius of the tee joint, U represents the flow velocity of the main pipe, S t A Style Luo Haer Number (Strouhal Number);
the calculation formula of the acoustic frequency of the hysteresis tube tee joint is as follows:
wherein L represents the length of the branch pipe, d represents the inner diameter of the branch pipe, c represents the sound velocity, and n represents the acoustic mode order;
s4, comparing the coupling condition of the modal frequencies of each order, and reflecting the possibility of resonance of each order;
s5, comprehensively evaluating the risk of vibration of the pipeline by combining the possibility of resonance and the severity of fatigue caused by resonance by using a risk matrix;
s6, for the pipeline with the high risk mode, design optimization is needed, and for the pipeline with the middle risk mode, the maximum speed node is used as a pre-service vibration measuring point, and the maximum stress point is used as a vibration fatigue evaluation point.
In one embodiment of the present invention, in step S4, a deviation of 10% is considered for the fixed frequency such as the main pump rotation frequency and the impeller frequency, and a deviation of 20% is considered for the frequency where the vortex shedding and the like may be locked in a certain range.
Compared with the prior art, the method for screening the pipeline vibration and selecting the monitoring points can be applied to vibration analysis and optimization in the design analysis of the pipeline of the nuclear power station, can also be used for guiding the vibration measurement and monitoring positions of the pipeline, and is also applicable to the vibration analysis and measurement of process pipelines of other various power stations or workshops; the method can optimize the pipeline design, reduce vibration problems, improve pertinence of vibration measurement and monitoring and realize the purpose of the invention.
The features of the present invention will be apparent from the following detailed description of the preferred embodiments, taken in conjunction with the accompanying drawings.
Drawings
FIG. 1 is a flow diagram of a method of screening and monitoring point selection for pipeline vibration of the present invention;
fig. 2 is a schematic structural view of a pipeline model according to the present invention.
Detailed Description
The invention is further described with reference to the following detailed drawings in order to make the technical means, the creation characteristics, the achievement of the purpose and the effect of the implementation of the invention easy to understand.
Examples
As shown in fig. 1, the method for screening and selecting monitoring points of the pipeline vibration comprises the following steps:
s1, calculating the speed and the stress of each node mode of a pipeline by taking a mode analysis result in pipeline design analysis, including the frequency of each mode, the mode displacement and the mode force of each node as inputs;
the modal velocity of node k is given by:
wherein χ is n，k Matrix form, ω representing nth order mode of k node n A circular frequency representing an nth order mode;
the formula of modal stress for node k:
wherein M is kx 、M ky Respectively representing bending moments in two directions of k node, W is section modulus of the pipeline, C 2 、K 2 Secondary stress and local stress coefficients in ASME BPVC fatigue calculation;
s2, taking a maximum stress node as a fatigue failure concern point, taking a maximum speed node as a vibration monitoring point, and calculating the ratio DS of the maximum modal stress and the maximum modal speed of the pipeline, wherein the DS value represents the magnitude of alternating bending moment stress under the same vibration speed and is used for reflecting the severity degree of fatigue caused by modal resonance of each stage;
s3, collecting and calculating potential vibration source frequencies, including pump frequency, impeller frequency, vortex shedding frequency, sound frequency and the like, wherein the pump frequency is determined according to the running rotation speed of the pump, and the impeller pressure pulsation frequency is equal to the main pump frequency multiplied by the number of blades of the impeller;
the vortex shedding frequency calculation formula of the stagnation pipe tee joint comprises the following steps:
wherein d represents the inner diameter of the branch pipe, r is the inner chamfer radius of the tee joint, U represents the flow velocity of the main pipe, S t A Style Luo Haer Number (Strouhal Number);
the calculation formula of the acoustic frequency of the hysteresis tube tee joint is as follows:
wherein L represents the length of the branch pipe, d represents the inner diameter of the branch pipe, c represents the sound velocity, and n represents the acoustic mode order;
s4, comparing the coupling condition of the modal frequencies of each order, and reflecting the possibility of resonance of each order; for fixed frequencies such as main pump rotation frequency and impeller frequency, 10% deviation is considered, and for frequencies such as vortex shedding which are possibly locked in a certain range, 20% deviation is considered;
s5, comprehensively evaluating the risk of vibration of the pipeline by combining the possibility of resonance and the severity of fatigue caused by resonance by using a risk matrix;
s6, for the pipeline with the high risk mode, design optimization is needed, and for the pipeline with the middle risk mode, the maximum speed node is used as a pre-service vibration measuring point, and the maximum stress point is used as a vibration fatigue evaluation point.
Fig. 2 is a graph of a calculation model of a power station pipeline, which can be subjected to modal analysis by various finite element software such as ANSYS, ABAQUS, PIPESTRESS, and output modal frequencies, modal patterns and modal loads of various orders. In this example, modal analysis was performed by using a pipe, and the results are summarized in table 1 by calculating the maximum modal stress, the maximum modal velocity, and the ratio DS thereof.
TABLE 1
And collecting and calculating potential vibration source frequencies, including pump frequency, impeller frequency and the like, and comparing the modal frequencies of each order with the coupling condition by calculating vortex shedding frequency, audio frequency and the like, wherein the results are summarized in table 2.
TABLE 2
The risk of vibration of the pipe is comprehensively evaluated by combining the possibility of resonance occurrence and the severity of fatigue caused by resonance by using a risk matrix. As shown in table 3. Wherein the resonance risk level of the 11 th order mode (23.217 Hz) is high, design optimization is needed to avoid the resonance frequency and reduce the DS level. In the resonance risk levels of the 1 st to 6 th order and 10 th order modes, the pre-service vibration measurement points are required to be determined according to the maximum speed points in table 1, and the vibration fatigue evaluation points are required to be determined according to the maximum stress nodes.
TABLE 3 Table 3
The foregoing has shown and described the basic principles and main features of the present invention and the advantages of the present invention. It will be understood by those skilled in the art that the present invention is not limited to the foregoing embodiments, which have been described in the foregoing embodiments and description merely illustrates the principles of the invention, and that various changes and modifications may be effected therein without departing from the spirit and scope of the invention as defined in the appended claims and their equivalents.
Claims (2)
1. The method for screening and selecting the monitoring points of the pipeline vibration is characterized by comprising the following steps of:
s1, calculating the speed and the stress of each node mode of a pipeline by taking a mode analysis result in pipeline design analysis, including the frequency of each mode, the mode displacement and the mode force of each node as inputs;
the modal velocity of node k is given by:
wherein χ is n，k Matrix form, ω representing nth order mode of k node n A circular frequency representing an nth order mode;
the formula of modal stress for node k:
wherein M is kx 、M ky Respectively representing bending moments in two directions of k node, W is section modulus of the pipeline, C 2 、K 2 Secondary stress and local stress coefficients in ASME BPVC fatigue calculation;
s2, taking a maximum stress node as a fatigue failure concern point, taking a maximum speed node as a vibration monitoring point, and calculating the ratio DS of the maximum modal stress and the maximum modal speed of the pipeline, wherein the DS value represents the magnitude of alternating bending moment stress under the same vibration speed and is used for reflecting the severity degree of fatigue caused by modal resonance of each stage;
s3, collecting and calculating potential vibration source frequencies, including pump frequency, impeller frequency, vortex shedding frequency and audio frequency, wherein the pump frequency is determined according to the running rotation speed of the pump, and the impeller pressure pulsation frequency is equal to the main pump frequency multiplied by the number of blades of the impeller;
the vortex shedding frequency calculation formula of the stagnation pipe tee joint comprises the following steps:
wherein d represents the inner diameter of the branch pipe, r is the inner chamfer radius of the tee joint, U represents the flow velocity of the main pipe, S t A Style Luo Haer Number (Strouhal Number);
the calculation formula of the acoustic frequency of the hysteresis tube tee joint is as follows:
wherein L represents the length of the branch pipe, d represents the inner diameter of the branch pipe, c represents the sound velocity, and n represents the acoustic mode order;
s4, comparing the coupling condition of the modal frequencies of each order, and reflecting the possibility of resonance of each order;
s5, comprehensively evaluating the risk of vibration of the pipeline by combining the possibility of resonance and the severity of fatigue caused by resonance by using a risk matrix;
s6, for the pipeline with the high risk mode, design optimization is needed, and for the pipeline with the middle risk mode, the maximum speed node is used as a pre-service vibration measuring point, and the maximum stress point is used as a vibration fatigue evaluation point.
2. The method of pipeline vibration screening and monitoring point selection according to claim 1, characterized in that in step S4, for the main pump rotation frequency, the fixed frequency of the impeller frequency, a deviation of 10% is considered, and for the frequency at which the vortex shedding is locked in a certain range, a deviation of 20% is considered.
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Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104408216A (en) * | 2014-09-04 | 2015-03-11 | 广东西屋康达空调有限公司 | Optimization method of vibration attenuation of pipeline |
| CN109582988A (en) * | 2017-09-29 | 2019-04-05 | 中国航发商用航空发动机有限责任公司 | The vibration stress monitoring foil gauge method for determining position of blade of aviation engine |
| CN111256805A (en) * | 2020-01-06 | 2020-06-09 | 武汉理工光科股份有限公司 | Method and system for transversely positioning vibration source of distributed optical fiber vibration sensor |
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| US10360326B2 (en) * | 2016-05-18 | 2019-07-23 | Solar Turbines Incorporated | Method for determining vibratory contact stress at a blade attachment |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104408216A (en) * | 2014-09-04 | 2015-03-11 | 广东西屋康达空调有限公司 | Optimization method of vibration attenuation of pipeline |
| CN109582988A (en) * | 2017-09-29 | 2019-04-05 | 中国航发商用航空发动机有限责任公司 | The vibration stress monitoring foil gauge method for determining position of blade of aviation engine |
| CN111256805A (en) * | 2020-01-06 | 2020-06-09 | 武汉理工光科股份有限公司 | Method and system for transversely positioning vibration source of distributed optical fiber vibration sensor |
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