CN212007508U - Device for measuring torsional vibration displacement of blade - Google Patents
Device for measuring torsional vibration displacement of blade Download PDFInfo
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- CN212007508U CN212007508U CN201921047132.4U CN201921047132U CN212007508U CN 212007508 U CN212007508 U CN 212007508U CN 201921047132 U CN201921047132 U CN 201921047132U CN 212007508 U CN212007508 U CN 212007508U
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Abstract
The utility model relates to a device for blade torsional vibration displacement measurement, including apex timing sensor, photoelectric receiving device, data acquisition processing module and signal processing system, by photoelectric receiving device output light current signal, light current signal produces analog signal after enlarging, filtering, transmits to data acquisition processing module, its characterized in that, apex timing sensor be two, same circumference position sets up two apex timing sensors of a set of two along the rotor axial on the rotating machinery machine casket, is used for measuring the time that certain branch blade tip inlet edge and gas outlet edge arrived apex timing sensor at same circle respectively; two blade tip timing sensors are arranged at the projection points of the maximum displacement position of the torsional resonance blade end on the horizontal line of the static position of the blade end. The utility model discloses can be used for realizing the measurement of blade torsional vibration displacement.
Description
Technical Field
The utility model belongs to rotating machinery state monitoring field, especially blade torsional vibration displacement measurement device based on apex timing principle.
Background
Important rotary machines such as aero-engines and steam turbines are core components of key equipment in the aerospace and industrial fields, such as military aircraft, commercial aircraft, generator sets, steam generating sets and the like. Particularly, the moving blade is used as a core element for the rotary machine to do work, and the working state of the moving blade directly influences the working efficiency and the conditions of safety, stability, long-period operation and the like of the important key equipment. At present, a rotating blade vibration measurement technology based on a blade tip timing principle is a typical non-contact measurement method, and the basic principle is that a certain number of sensors are arranged on a rotating mechanical casing, the arrival time of the rotating blade passing through the sensors is measured, and measurement of blade vibration parameters such as vibration amplitude, vibration frequency and vibration phase is achieved through a relevant identification algorithm. Compared with the traditional off-line blade state detection method and the on-line detection methods such as a strain gauge method, a frequency modulation method, a sound method and the like, the tip timing technology has the advantages of non-contact measurement, real-time on-line monitoring, measurement of all blades and the like, so that the method has better engineering practicability.
In one aspect, the blade is one of the core components of a large rotating machine. Taking an aircraft engine as an example, the working environment where the blades are located under the working condition is severe, and the blades are continuously influenced by the air flow exciting force, the atmospheric temperature difference, the high temperature and other environments besides the centrifugal force. These external conditions generate relatively complicated cyclic stress on the rotating blades of the engine, and when the frequency of the external excitation force is equal to or close to a certain order natural frequency of the blades, the blades may have faults such as blade cracks or blade fractures due to resonance. According to statistics, the faults caused by mechanical vibration account for more than 60% of the total faults of the aero-engine, the blade vibration faults account for more than 70% of the total faults of the aero-engine, and the blade vibration faults are the important reasons for the faults of the aero-engine, so that the vibration characteristics of the blades are researched, the operation conditions of the blades are monitored in real time on line, and the method has important practical significance in the aspects of research and development tests, state monitoring, fault diagnosis and the like of important rotary machines such as the aero-engine, a steam turbine and the like.
On the other hand, when the blade works, the blade is mainly subjected to the action of external periodically-changed excitation force to generate forced vibration, and the blade vibration can be divided into three vibration modes of bending vibration, torsional vibration and bending-torsion composite vibration according to different vibration expression forms. The same blade has a plurality of different resonance frequencies which are divided into a first-order resonance and a second-order resonance … … from small to large, when the external excitation force frequency is consistent with a certain order resonance frequency of the blade, the blade is excited to generate resonance, and the vibration modes corresponding to the different-order resonance are not necessarily the same. The utility model discloses in be not more than the vibration of its one-order resonance frequency with blade vibration frequency and call the low order vibration, the vibration that blade vibration frequency is greater than its one-order resonance frequency is called the high order vibration. The mode shape of the first order resonance of the blade is usually bending vibration, also called first order bending vibration. The first-order bending vibration is the main reason for generating cracks at the root part of the blade and breaking the root part, the harmfulness is high, and the measurement method is relatively easy to realize, so that the research on the first-order bending vibration is deep at home and abroad. Existing tip timing measurements, including fast vector endtrace methods[1]Two parameter method[2]Self-returning method[3]And arbitrary angular distribution method based on sensors[4]And the like, only one blade tip timing sensor is arranged at the same circumferential position of the rotating mechanical casing, so that the measurement of the bending vibration displacement of the blade can be realized only, and the measurement of the torsional vibration displacement of the blade cannot be realized.
On the other hand, the vibration modes of the high-order vibration of the blade comprise three vibration modes of bending vibration, torsional vibration and bending-torsional composite vibration, blade cracks or corner drop faults caused by the torsional vibration often occur, but the high-order vibration of the blade has the measurement problems of small amplitude, complex vibration mode, difficult sensor layout and the like, few researches on the measurement methods of the high-order vibration parameters of the blade are conducted at home and abroad, and particularly, the measurement methods of the parameters such as the torsional vibration displacement of the blade are not reported.
[1]I.Y.Zablotsky and Yu.A.Korostelev.Measurement of resonance vibrations of turbine blades with the ELURA device[J].Energomashinostroneniye,1970,Vol.2:36-39.
[2]S Heath.A New Technique for Identifying Synchronous Resonances Using Tip-Timing[J].Journal of Engineering for Gas Turbines and Power,2000,122(2):219-225.
[3]J.Gallego-Garrido,G.Dimitriadis,and J.R.Wright,A Class of Methods for the Analysis of Blade Tip Timing Data from Bladed Assemblies Undergoing Simultaneous Resonances—Part I:Theoretical Development[J]. International Journal of Rotating Machinery,2007,Vol.2007:1-11.
[4] Blade tip timing-based rotary blade vibration detection and parameter identification technology [ D ]. doctor academic thesis, tianjin university, 2011.
SUMMERY OF THE UTILITY MODEL
The utility model aims at providing a be used for blade torsional vibration displacement measurement's device to overcome the unable shortcoming of measuring blade torsional vibration displacement of current apex timing measurement device. The technical scheme of the utility model as follows:
a device for measuring torsional vibration displacement of a blade comprises blade tip timing sensors, photoelectric receiving devices, a data acquisition processing module and a signal processing system, wherein the photoelectric receiving devices output photoelectric current signals, the photoelectric current signals are amplified and filtered to generate analog signals, the analog signals are transmitted to the data acquisition processing module, the blade tip timing sensors are divided into two parts, two groups of blade tip timing sensors are arranged on a rotating mechanical casing at the same circumferential position along the axial direction of a rotor and are respectively used for measuring the time of an air inlet edge and an air outlet edge of the blade end of a certain blade reaching the blade tip timing sensors in the same circle; two blade tip timing sensors are arranged at the projection points of the maximum displacement position of the torsional resonance blade end on the horizontal line of the static position of the blade end.
The utility model overcomes current apex timing measurement method can't measure the shortcoming of blade torsional vibration displacement, a blade torsional vibration displacement measuring device based on apex timing principle is proposed, set up two apex timing sensors along the rotor axial in the same circumference position of rotating machinery case, measure the time of certain blade tip inlet edge and gas outlet edge when two apex timing sensors are reachd in same circle respectively, if the software of assisting signal processing system again, can realize the accurate measurement of blade torsional vibration displacement.
Drawings
FIG. 1 shows a schematic diagram of a tip timing principle measurement scheme
FIG. 2 shows a blade torsional vibration displacement measurement configuration diagram
FIG. 3 shows a first order torsional vibration mode diagram of a blade
FIG. 4 shows a top view of a blade torsional vibration displacement measurement sensor positioning
FIG. 5 shows a blade torsional vibration displacement measurement plan view
The reference numbers in the figures illustrate:
in fig. 1, 1 is a tip timing sensor; 2 is a rotating machinery case; 3 is a blade;
in fig. 2, 4 is the leading edge tip timing sensor; 5 is a timing sensor of the air outlet edge blade tip; 6 is a blade end air inlet edge, 7 is a blade end air outlet edge, and 8 is a signal processing system;
in FIG. 3, 9 is the leaf end; 10 is a vibration nodal line; 11 is a vibration node;
in fig. 4, 4 is the leading edge tip timing sensor; 5 is a timing sensor of the air outlet edge blade tip; 11 is a vibration node; 12 is the maximum displacement position of the torsional resonance blade end; 13 is the maximum deviation angle of the torsional resonance blade end; 14 is the displacement of the air inlet edge of the torsional resonance blade end; 15 is the displacement of the air outlet edge at the torsional resonance blade end; 16 is the tip rest position;
in fig. 5, 2 is a rotary machine casing; 4, a gas inlet edge blade tip timing sensor; 5 is a timing sensor of the air outlet edge blade tip; 12 is the maximum displacement position of the torsional resonance blade end; 16 is the tip rest position; 17 is the real-time position of the torsional vibration blade end; 18 is the rotor axial horizontal line; 19 is a torsional vibration blade tip deviation angle; 20, measuring the displacement of the air inlet edge of the blade end by a sensor during torsional vibration; 21, measuring the displacement of the air outlet edge of the blade end by a sensor during torsional vibration; 22 is the true blade end air inlet edge displacement during torsional vibration; and 23, the displacement of the air outlet edge of the real blade end during torsional vibration.
Detailed Description
The following detailed description of the steps for making and operating the present invention, as embodied in the invention, is not intended to be exhaustive or to be construed as the only form in which the present invention may be constructed, but is intended to include within its scope other embodiments for performing the same function.
The utility model discloses in be called the tip with the blade top, the circumferencial direction of rotating machinery casket is called circumference, and the one side that the blade was facing air current direction is called the contained side, and the one side that the blade was facing air current direction dorsad is called out the contained side, and the blade end edge is called the blade torsional vibration displacement through the difference of the circumferential distance that two apex timing sensors in contained side and the contained side produced in same circle during torsional vibration, combines the specification drawing detailed description below the preferred embodiment of the utility model.
The structure measurement of the blade tip timing principle is shown in figure 1, and the existing blade tip timing measurement method[1-4]Only one blade tip timing sensor 1 is arranged at the same circumferential position of a rotating mechanical casing 2, when each blade 3 rotates and passes through the blade tip timing sensor 1, an arrival pulse signal is generated, and a signal processing system realizes measurement of bending vibration displacement of the blade by using the pulse time when the blade 3 arrives at the blade tip timing sensor 1;
the blade torsional vibration displacement measurement structure is shown in fig. 2, the utility model provides a method is at the same circumferential position of rotating machinery casket, along rotor axial installation two sets of apex timing sensor, respectively when low rotational speed blade does not take place the vibration and high rotational speed blade takes place torsional vibration, measure blade end air inlet edge 6 and arrive air inlet edge apex timing sensor 4 and blade end air outlet edge 7 and arrive the time of air outlet edge apex timing sensor 5; the tip timing sensor adopts an optical fiber bundle type sensor consisting of a transmitting optical fiber and a plurality of receiving optical fibers, the laser emits laser through the transmitting optical fiber, when the air inlet edge 6 and the air outlet edge 7 of the blade end sequentially reach the air inlet edge tip timing sensor 4 and the air outlet edge tip timing sensor 5, the plurality of receiving optical fibers can receive reflected light signals of the blade end and transmit the reflected light signals to the photoelectric receiving device, the photoelectric receiving device outputs photocurrent signals, the photocurrent signals are amplified and filtered to generate standard analog signals and are transmitted to the data acquisition processing module, and the signal processing system 8 realizes the measurement of the arrival time of the blade by acquiring the generation time of the photocurrent signals.
The first-order torsional vibration mode of the blade is shown in fig. 3, when the blade vibrates, a connecting line formed by each point with zero vibration displacement on the blade body is called a vibration nodal line, the intersection point of the vibration nodal line and the blade end is called a vibration node, when the blade vibrates in the first-order torsional vibration, the air inlet edge and the air outlet edge of the blade end do relative torsional motion around the vibration nodal line 10 of the blade, the vibration nodal line 10, the vibration node 11, the resonance frequency, the resonance amplitude and other parameters of the blade can be obtained through the natural frequency test of the blade, and usually the vibration nodal line when the blade vibrates in the torsional vibration is not necessarily in the middle position of the blade body, so the vibration node 11 is not necessarily positioned in the middle point position of the;
the positioning of the blade torsional vibration displacement measurement sensor is shown in fig. 4, the blade comprises two conditions of torsional non-resonance and torsional resonance when torsional vibration occurs, a certain blade to be measured is selected, the blade end of the blade takes the blade end static position 16 as the central position when torsional vibration occurs, periodic torsional motion is performed between the maximum displacement positions 12 of the two torsional resonance blade ends, in order to ensure that the blade tip timing sensor can accurately measure time signals of the blade end air inlet side and the blade tip timing sensor reaching the blade tip timing sensor under the conditions that the blade is subjected to torsional non-resonance and torsional resonance, the positioning of the two blade tip timing sensors needs to be determined by combining torsional resonance parameters of the blade, the maximum displacement position 12 of the torsional resonance blade end and the maximum deviation angle 13 of the torsional resonance blade end can be obtained through a natural frequency test of the blade, the length of the blade end can be obtained by a design drawing, and alpha is set as the maximum deviation angle 13 of the, o is a vibration node 11, a line segment AB is the length of the blade end, E is the installation position of the inlet edge blade tip timing sensor 4, F is the installation position of the outlet edge blade tip timing sensor 5, and h is1For displacement of the inlet edge of the torsional resonance blade end by 14, h2The displacement is 15 for the air outlet edge of the torsional resonance blade end;
when the blade is in a torsional resonance condition, the real-time position of the blade end periodically changes between the maximum displacement positions 12 of the two torsional resonance blade ends, the projection of the maximum displacement position 12 of the torsional resonance blade end on the horizontal line of the static position 16 of the blade end is a line segment EF, the length of the EF is the minimum value of the projection line segments of the real-time positions of all the blade ends on the horizontal line of the static position 16 of the blade end in the torsional vibration process of the blade, the maximum deviation angle 13 of the torsional resonance blade end is the maximum value of the deviation angles of all the blades in the torsional vibration process, the inlet edge displacement 14 and the outlet edge displacement 15 of the torsional resonance blade end are the maximum values in the torsional displacement of all the blades in the torsional vibration process, the inlet edge blade tip timing sensor 4 is installed at the point E, the outlet edge blade tip timing sensor 5 is installed at the point F, so that under the condition that the blade is in the, the two blade tip timing sensors can sample all arrival time signals of the blade tips, and the positioning method is called as a torsional resonance projection method by the utility model;
when the blade is in a torsional non-resonance condition, the real-time position of the blade end carries out periodic torsional motion between the maximum displacement positions 12 (not including the maximum displacement positions 12) of the two torsional resonance blade ends, the projection of the real-time position of the blade end on the horizontal line of the static position 16 of the blade end periodically changes between a line segment EF (not including points E and F) and a line segment AB, and the two blade tip timing sensors positioned at the points E and F can still sample all time signals from the blade end to the two blade tip timing sensors;
because the situation that the blade is in torsional non-resonance or torsional resonance when passing through the blade tip timing sensor cannot be confirmed, if the installation positions of the two blade tip timing sensors are moved from the point E and the point F to the point O, although all time signals of the torsional vibration blade end reaching the two blade tip timing sensors can still be sampled, when the blade is in the torsional non-resonance situation and the vibration displacement of the blade is small, the time difference signal of the blade end passing through the two blade tip timing sensors is also small, and at the moment, if the precision of a signal processing system is not high enough, the situation that the signal cannot be sampled can occur; if the mounting positions of the two blade tip timing sensors are respectively moved to the point A and the point B from the point E and the point F, the situation of signal sampling leakage can occur when the blades generate torsional resonance or torsional non-resonance but the vibration displacement is larger, the sensor positioning method can ensure that the maximum time difference signal or the larger time difference signal when the blades reach the two blade tip timing sensors is acquired on the premise that the signal sampling leakage does not occur, so the point E and the point F determined by using the torsional resonance projection method can be used as the optimal positioning points of the sensor for measuring the torsional vibration of the blades based on the blade tip timing principle;
(V) blade torsional vibration displacement measurement As shown in FIG. 5, set Ωn1The low rotational angular velocity, omega, of the rotor when the blade is not vibratingn2The high speed rotational angular velocity of the rotor when the blades are subjected to torsional vibration, n is the number of revolutions of the rotor, and the blade end rest position 16 is not parallel to the axial horizontal line 18 of the rotor in general;
1. when the rotor is at angular velocity omegan1When the low-speed rotating blade does not vibrate, the blade end of the blade is always positioned at the blade end static position 16 when rotating to pass through the inlet edge blade tip timing sensor 4 and the outlet edge blade tip timing sensor 5, so that the time difference delta t between each circle of the blade and the inlet edge blade tip timing sensor 4 and the outlet edge blade tip timing sensor 5 is realizedn10, the torsional vibration displacement is 0;
2. when the rotor is at angular velocity omegan2When the high-speed rotating blade generates torsional vibration, the real-time position of the blade end of the blade when the blade end rotates to pass through the inlet edge blade tip timing sensor 4 and the outlet edge blade tip timing sensor 5 is periodically changed between the maximum displacement positions 12 of the two torsional resonance blade ends of the blade, the arbitrary torsional vibration blade end real-time position 17 when the blade rotates to pass through the two blade tip timing sensors is selected without losing generality, and the time difference delta t of the blade end reaching the inlet edge blade tip timing sensor 4 and the outlet edge blade tip timing sensor 5 is actually measured in the nth circlen2The blade may be calculated as Ωn2When torsional vibration occurs in high-speed rotation and passes through the two blade tip timing sensors, the circumferential arc length of the blade tip passing along with the rotation of the rotor is as follows:
Ln2＝Ωn2RΔtn2，n＝1.2.3... (1)
wherein R is the radius of rotation of the blade tip due to Δ tn2Are usually small, so that the blade tipAt Δ tn2The circumferential arc length passing along with the rotation of the rotor in the time difference is approximately equal to the sum of the displacement 20 of the air inlet edge of the blade end measured by the sensor during the torsional vibration and the displacement 21 of the air outlet edge of the blade end measured by the sensor during the torsional vibration, namely:
Ln2＝Ωn2RΔtn2＝h3+h4，n＝1.2.3... (2)
in the formula, h3The displacement of the air inlet edge of the blade end measured by the sensor during torsional vibration is 20 h4The displacement 21 of the air inlet side of the blade end is measured by a sensor during torsional vibration, the displacement 20 of the air inlet side of the blade end is measured by the sensor during torsional vibration and the displacement 21 of the air outlet side of the blade end and the distance EF between the sensors during two blade tips are measured by the sensor during torsional vibration by combining the displacement 19 of the air inlet side of the blade end during torsional vibration, so that the value of the displacement 19 of the blade end during torsional vibration can be calculated:
in the formula, d is the distance between the two blade tip timing sensors, namely the length of a line segment EF;
3. because the positioning of the two blade tip timing sensors is based on the torsional resonance projection method, the arrival time of the edge of the blade end is not measured by the inlet edge blade tip timing sensor 4 and the outlet edge blade tip timing sensor 5, and the L calculated by the formula (2)n2Not the true torsional vibration displacement of the blade; the following trigonometric functions exist between the torsional vibration blade end deviation angle 19, the displacement of the air inlet edge of the blade end measured by the sensor during torsional vibration 20, the displacement of the air outlet edge of the blade end measured by the sensor during torsional vibration 21, the displacement of the air inlet edge of the real blade end during torsional vibration 22, the displacement of the air outlet edge of the real blade end during torsional vibration 23, the distance between the timing sensors of the two blade tips and the length of the blade end:
in the formula, h5For the true tip leading edge displacement 22 during torsional vibration,h6the displacement of the true blade end air outlet edge 23 in torsional vibration, p is the length of the blade end line segment AB, and the blade has the angular velocity omega in combination with the trigonometric function relationship in the formula (4)n2The torsional vibration displacement generated by the timing sensors rotating at high speed through the two blade tips is as follows:
the maximum deviation angle alpha of the torsional resonance blade end can be obtained by blade natural frequency tests, and the rotor rotation angular velocity omegan1And Ωn2The rotor speed measurement system can be used for obtaining the time difference delta t from the blade end to the two blade tip timing sensors through actual measurement, the rotating radius R of the blade end, the length p of the blade end and the distance d between the two blade tip timing sensors can be obtained through a design drawingn1And Δ tn2Can be obtained by the actual measurement of a blade tip timing sensor.
Claims (1)
1. A device for measuring torsional vibration displacement of a blade comprises two tip timing sensors, a photoelectric receiving device, a data acquisition processing module and a signal processing system, wherein the photoelectric receiving device outputs a photocurrent signal which is amplified and filtered to generate an analog signal and transmitted to the data acquisition processing module; two blade tip timing sensors are arranged at the projection points of the maximum displacement position of the torsional resonance blade end on the horizontal line of the static position of the blade end.
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN114033732A (en) * | 2021-11-10 | 2022-02-11 | 中国航发沈阳发动机研究所 | Rotor blade during operation twists reverse angle measurement system |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN114033732A (en) * | 2021-11-10 | 2022-02-11 | 中国航发沈阳发动机研究所 | Rotor blade during operation twists reverse angle measurement system |
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