CN113720768B - Experimental test system and method for dynamic characteristics of dry friction damping - Google Patents
Experimental test system and method for dynamic characteristics of dry friction damping Download PDFInfo
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Abstract
The invention discloses an experimental test system and method for dynamic characteristics of dry friction damping, wherein the experimental test system comprises: moving the flat plate; the piezoelectric holding device and the motion transmitting mechanism are fixedly arranged on the movable flat plate; the piezoelectric holding device and the motion transmission mechanism are connected through a piezoelectric actuator; the motion transmitting mechanism is fixedly provided with a first simulation piece clamp; the first simulation piece clamp is provided with a first blade root platform simulation piece; fixing the flat plate; the fixed flat plate is fixedly provided with a signal holding device; the signal holding device is provided with a voltage power sensor; the piezoelectric force sensor is connected with a second simulation piece clamp through a force transmitting mechanism, and a second blade root platform simulation piece is installed on the second simulation piece clamp; laser vibrometer. The method combines experimental research and contact parameter estimation, specifically quantifies and evaluates the motion characteristic of the friction damper, and can carry out systematic research on the dynamic characteristic of dry friction damping of the gas turbine blade material.
Description
Technical Field
The invention belongs to the technical field of testing of a dry friction damping mechanism of a metal material, and particularly relates to an experimental testing system and method for dynamic characteristics of dry friction damping.
Background
For a gas turbine compressor and a turbine blade with a dry friction damping structure, the friction action between contact surfaces is the key for dissipating the vibration energy of the blade, and the deep research on the dynamic characteristics of the friction damping between the contact surfaces is very important for revealing the dry friction damping vibration characteristics of the turbine blade. Due to the highly complex nonlinear characteristic of dry friction, friction models proposed by theoretical analysis are simplified to a certain extent and are difficult to accurately solve, so experimental tests are still an important means for determining the dynamic characteristic of the contact surface of the blade root platform and the friction damper.
At present, the researchers have carried out preliminary research on the dynamic characteristics of the friction damping between the contact surfaces of the metal materials by adopting an experimental method, but on one hand, the research is mostly directed to materials such as common carbon steel, aluminum alloy and the like, and the research on the high-temperature nickel-based alloy steel materials commonly used for the blades of the gas turbines is less. The high-temperature nickel-based alloy steel material has high specific strength, high elastic modulus and small thermal expansion coefficient, and is not easy to deform compared with common carbon steel under the same excitation condition, so that displacement signals are difficult to accurately capture by adopting a common acquisition method; and the friction hysteresis curve obtained by testing a common carbon steel material has larger characteristic difference with the high-temperature nickel-based alloy, and cannot be directly applied, so that an experimental test system capable of accurately generating and measuring the dry friction damping dynamic characteristic of the high-temperature nickel-based alloy material of the gas turbine needs to be designed aiming at the high-temperature nickel-based alloy material of the gas turbine. On the other hand, the whole influence of the friction damper on the blade is mostly researched from the aspects of vibration reduction amplitude and resonance frequency shift in the current experiment, the black box-like method is used for evaluating the capacity of the friction damper for reducing resonance displacement, and contact characteristic parameters are not obtained on the basis of direct experimental research, so that the motion characteristic of the friction damper cannot be specifically and quantitatively evaluated; and each experiment only carries out measurement research aiming at respective working conditions, and a frictional contact characteristic parameter database suitable for engineering technology is difficult to form, and the parameters have important influence on the dry friction damping vibration characteristics of the gas turbine blade, and further intensive research is needed.
Disclosure of Invention
The invention aims to provide a system and a method for testing the dynamic characteristic of dry friction damping in an experiment, so as to solve one or more technical problems. The invention provides an experimental test system capable of accurately measuring the dry friction damping dynamic characteristics of a high-temperature nickel-based alloy material of a gas turbine blade, which combines experimental research and contact parameter estimation, specifically quantifies and evaluates the motion characteristics of a friction damper, and can systematically research the dynamic characteristics of the dry friction damping of the gas turbine blade material.
In order to achieve the purpose, the invention adopts the following technical scheme:
the invention relates to an experimental test system for dynamic characteristics of dry friction damping, which comprises:
the movable flat plate is detachably and fixedly arranged on a preset bottom plate or a preset base; the piezoelectric holding device and the motion transmitting mechanism are fixedly arranged on the movable flat plate; the piezoelectric holding device and the motion transmission mechanism are connected through a piezoelectric actuator; the motion transmitting mechanism is fixedly provided with a first simulation piece clamp; the first simulation piece clamp is provided with a first blade root platform simulation piece; wherein the first root platform simulator is provided with a contact surface for contacting a friction damper;
a fixing plate for fixing and mounting on a predetermined base plate or base; the fixed flat plate is fixedly provided with a signal holding device; the signal holding device is provided with a voltage power sensor; the piezoelectric force sensor is connected with a second simulation piece clamp through a force transmitting mechanism, and a second blade root platform simulation piece is installed on the second simulation piece clamp; wherein the second root platform simulation element is provided with a contact surface for contacting a friction damper; the static load simulation device is used for applying centrifugal force load to the friction damper;
and the laser vibration meter is used for measuring the contact area of the first blade root platform simulation piece and the friction damper and the displacement of the contact area of the second blade root platform simulation piece and the friction damper.
A further development of the invention is that the contact surfaces of the first and second root platform simulators are provided with contact rails.
A further improvement of the present invention is that the moving plate, the piezoelectric holding device, and the motion transmitting mechanism are each provided with a mounting chute.
A further development of the invention is that the force transmission mechanism is two mutually perpendicular hollow geometries, rigid in the axial direction and flexible in the transverse direction.
The invention further improves the method and also comprises the following steps: the friction damper is a sphere, a cylinder, a unilateral semi-cylinder or a bilateral semi-cylinder.
A further development of the invention is that the contact of the first root platform simulator with the friction damper and the second root platform simulator with the friction damper is in the form of point-to-surface, line-to-surface or surface-to-surface.
In a further development of the invention, the laser emitted by the laser vibrometer is directed perpendicularly onto the contact areas of the first blade root platform simulation and the friction damper and of the second blade root platform simulation and the friction damper, respectively.
The invention relates to an experimental test method for dynamic characteristics of dry friction damping, which is based on the experimental test system and comprises the following steps:
according to the plane rectangular coordinate, the vertical direction is the y-axis direction, and the horizontal direction is the x-axis direction; adjusting the relative installation positions of the movable flat plate and the fixed flat plate to enable the piezoelectric actuator to output sinusoidal simple harmonic displacement signals in the vertical direction or the horizontal direction, enabling the force transmitting mechanism to decompose the received mechanical signals into normal positive pressure signals and horizontal direction signals, and enabling the piezoelectric power sensor to acquire the normal positive pressure signals;
obtaining corresponding friction hysteresis loops under the conditions of different preset contact surface materials, centrifugal loads and input displacement;
obtaining characteristic parameters reflecting the motion characteristics of the contact surface based on the obtained friction hysteresis loop;
establishing a frictional contact characteristic parameter database based on the characteristic parameters; and linear equivalence and quantitative evaluation of the dynamic characteristics of the dry friction damping are realized based on the frictional contact characteristic parameter database.
In a further development of the invention, the characteristic parameters reflecting the movement characteristics of the contact surface include: tangential contact stiffness coefficient, material friction coefficient, equivalent stiffness coefficient and equivalent damping coefficient;
wherein, the tangential contact rigidity coefficient calculation expression is as follows:
kd＝(kd1+kd2)/2，
in the formula, kdAs coefficient of tangential contact stiffness, kd1For measuring the slope, k, of the initial stage of micromotion slip during loading in the hysteresis curved2The slope of the initial stage of the micro-motion slip in the unloading process in the hysteresis curve obtained by measurement;
according to the friction hysteresis loop obtained by experimental measurement, the positive and negative absolute values f 'of the friction force in the integral macroscopic sliding stage'mAnd f ″)mTaking and averaging to obtain fmAnd then dividing the obtained value by the corresponding positive pressure load N to obtain a material friction coefficient mu, wherein the expression is as follows:
calculating the coefficient of friction mu of the contact surface of the first root platform simulatorLWhen N is equal to FL(ii) a When calculating the coefficient of friction mu of the contact surface of the second leaf root platform simulationRWhen N is equal to FR(ii) a Wherein, FLSimulating a member normal force for the first root platform, FRSimulating a normal force for the second leaf root platform;
according to the linearization criterion, the contact surface is simplified into a no-mass spring damping system, the friction force between the contact surfaces is calculated by the superposition of the elastic force and the damping force, and the expression is as follows:
wherein, KeqIs the equivalent stiffness coefficient between the friction contact surfaces, CeqF is the friction force between the contact surfaces, and u is the relative displacement between the contact surfaces;
according to the energy dissipation principle, friction dissipation energy is the area surrounded by the hysteresis loop, and the friction hysteresis loop is subjected to surface integration to obtain the equivalent stiffness coefficient K between the friction contact surfaceseqAnd equivalent damping coefficient CeqThe expressions are respectively:
wherein f (T, θ) represents a friction hysteresis loop, TmThe relative displacement amplitude corresponding to the hysteresis loop.
The invention is further improved by being used for experimental test of the dry friction damping dynamic property of the high-temperature nickel-based alloy material of the gas turbine blade.
Compared with the prior art, the invention has the following beneficial effects:
in the system, the piezoelectric actuator, the piezoelectric sensor and the laser vibration meter are respectively used as a signal generating device, a signal receiving device and a signal measuring device, so that high-precision generation and collection of millimeter-level displacement signals and mechanical signals in an experiment can be ensured; the piezoelectric holding device, the signal holding device, the motion transmitting mechanism and the force transmitting mechanism are adopted, so that the nondestructive and stable transmission of the experiment signal can be ensured. The invention directly measures and collects the displacement and force signals on the contact surface of the blade root platform and the damper, thereby better knowing the motion characteristic of the friction damper. Specifically, in the system of the present invention, a piezoelectric actuator is mounted between the piezoelectric holding device and the motion transducing mechanism for generating a desired sinusoidal simple harmonic displacement signal; the piezoelectric holding device is used for ensuring that the direction of the displacement signal input by the piezoelectric actuator is single and stable and transmitting the displacement signal to the first blade root platform simulation piece; the motion transmitting mechanism is used for ensuring that the magnitude of the displacement signal input by the piezoelectric actuator is accurate and lossless and transmitting the displacement signal to the first blade root platform simulation piece.
In the invention, the contact surface is provided with the contact rail for contacting with the axial surface of the friction damper, and the medium-pressure load can be converted into the high-pressure load on the contact plane of the friction damper; the contact rails are adapted for axial positioning contact with the friction damper.
In the invention, the force transmission mechanism is two mutually vertical hollow geometric bodies with two elongated sides, is rigid in the axial direction and can be regarded as flexible in the transverse direction (the rigidity ratio between the axial direction and the transverse direction >100), and is respectively connected with the piezoelectric force sensor, thereby ensuring the accurate transmission of output mechanical information; the piezoelectric force sensor has enough load range and small signal loss, receives the mechanical signal of the second blade root platform simulation piece and outputs the result.
In the invention, the friction damper is a sphere, a cylinder, a unilateral semi-cylinder or a bilateral semi-cylinder and is used for forming surface-surface contact, line-surface contact or point-surface contact with the simulation parts on two sides.
In the experimental test method for the dynamic characteristics of the dry friction damper, the experiment is combined with parameter analysis, and the evaluation index of the friction damper is quantized; the experimental data and the analysis parameters form a database, so that engineering application is facilitated. Specifically, the invention directly measures and collects the displacement and force signals on the contact surface of the blade root platform and the damper, thereby better knowing the motion characteristics of the friction damper, and realizing the dual targets of direct experimental research and contact parameter estimation based on obtaining the friction hysteresis loop and the contact parameters such as the friction coefficient, the tangential contact stiffness coefficient, the equivalent friction coefficient and the equivalent damping coefficient.
In the method, the complex nonlinear problem of the frictional contact is converted into equivalent linear parameters for quantitative evaluation, the combination of direct experimental study and contact parameter estimation is realized, the dynamic characteristics of the dry friction damping of the high-temperature nickel-based alloy material of the gas turbine blade are revealed, a frictional contact characteristic parameter database suitable for engineering technology is formed, and important references are provided for the design and application of the frictional damper of the gas turbine blade.
The invention provides an experimental test method capable of accurately measuring the friction damping dynamic characteristics of a high-temperature nickel-based alloy material of a gas turbine. The method can realize the accurate measurement of the characteristic parameters of the dry friction damping contact surface of the high-temperature nickel-based alloy material of the gas turbine blade, and can analyze the influence of the change of input conditions such as excitation frequency, contact pressure, geometric shape, centrifugal load, motion direction and the like on the contact state.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art are briefly introduced below; it is obvious that the drawings in the following description are some embodiments of the invention, and that for a person skilled in the art, other drawings can be derived from them without inventive effort.
FIG. 1 is a schematic top view of a gas turbine blade material dry friction damping dynamics testing system according to an embodiment of the present invention;
FIG. 2 is a schematic diagram of a front view of the system shown in the embodiment of FIG. 1;
FIG. 3 is a schematic view of an arrangement of adjacent blades moving in phase in an embodiment of the present invention; wherein, fig. 3(a) is a schematic diagram of a test system for the in-phase motion of adjacent blades, and fig. 3(b) is a partial schematic diagram of the motion displacement of the friction damper; FIG. 3(c) is an exploded view of the displacement of adjacent blades in phase;
FIG. 4 is a schematic illustration of an arrangement of adjacent blades moving out of phase in an embodiment of the present invention; wherein FIG. 4(a) is a schematic view of a test system with adjacent blades moving out of phase, and FIG. 4(b) is a partial schematic view of the movement displacement of the friction damper; FIG. 4(c) is an exploded view of adjacent blades displaced out of phase;
FIG. 5 is a partial schematic view of a root platform simulator contacting a rail in accordance with an embodiment of the invention;
FIG. 6 is a schematic illustration of various friction dampers in cooperation with a blade root platform in accordance with embodiments of the present invention; wherein, fig. 6(a) is a schematic view when the friction damper is in the form of a sphere or a cylinder, fig. 6(b) is a schematic view when the friction damper is in the form of a one-sided semi-cylinder, fig. 6(c) is a schematic view when the friction damper is in the form of a one-sided semi-cylinder, and fig. 6(d) is a schematic view when the friction damper is in the form of a double-sided semi-cylinder;
FIG. 7 is a schematic illustration of an analysis of in-phase (out-of-phase) relative motion between blade root platforms on two sides, for a blade root platform simulator selected as a research object in an embodiment of the present invention; wherein, fig. 7(a) is a schematic diagram of the force analysis of the blade root platform, fig. 7(b) is a diagram of the relationship between the force and the displacement of the blade root platform, and fig. 7(c) is a friction hysteresis loop of the relative motion between the blade root platforms at two sides in phase (out of phase);
FIG. 8 is a schematic diagram illustrating an analysis of the relative motion between the friction damper and the blade root platform interface when the friction damper is selected as the subject of the present invention; wherein, fig. 8(a) is a schematic diagram of the analysis of the contact surface stress, fig. 8(b) is a graph of the relationship between the contact surface stress and the displacement, and fig. 8(c) is a friction hysteresis loop of the relative motion between the obtained friction damper and the contact surface of the blade root platform;
FIG. 9 is a schematic flow chart of a method for testing the dry friction damping dynamic characteristics of a gas turbine blade material according to an embodiment of the invention;
in FIGS. 1-9, 1-move the plate; 2-a piezoelectric holding device; 3-a motion transmitting mechanism; 4-a piezoelectric actuator; 5-a first root platform simulator; 6-a first mock piece clamp; 7-a first chute; 8-a second chute; 9-fixing the flat plate; 10-a signal holding means; 11-a piezoelectric force sensor; 12-a force transmitting mechanism; 13-a second leaf root platform simulation; 14-a second mock piece clamp; 15-laser vibration meter; 16-a friction damper; 17-a contact track; 18-steel wire.
Detailed Description
In order to make the purpose, technical effect and technical solution of the embodiments of the present invention clearer, the following clearly and completely describes the technical solution of the embodiments of the present invention with reference to the drawings in the embodiments of the present invention; it is to be understood that the described embodiments are only some of the embodiments of the present invention. Other embodiments, which can be derived by one of ordinary skill in the art from the disclosed embodiments without inventive faculty, are intended to be within the scope of the invention.
The invention provides an experimental test system capable of accurately measuring the dry friction damping dynamic characteristics of a high-temperature nickel-based alloy material of a gas turbine blade, which combines experimental research and contact parameter estimation, specifically quantifies and evaluates the motion characteristics of a friction damper, can perform system research on the dynamic characteristics of the dry friction damping of the material of the gas turbine blade, constructs experimental data and contact parameters into a friction contact characteristic parameter database, and is convenient for direct calling and application in the industrial design analysis and vibration damping research of the aviation-grade blade.
Referring to fig. 1 and 2, in the system for testing the dry friction damping dynamic characteristics of the gas turbine blade material according to the embodiment of the invention, the whole system can be built on a base plate with a positioning screw hole, and mainly comprises a motion generation module, a signal measurement module and a friction damper. Illustratively, in a rectangular plane coordinate system, the vertical direction is changed to the y direction, and the horizontal direction is changed to the x direction.
The motion generation module includes: a moving plate 1, a piezoelectric holding device 2, a motion transmission mechanism 3, a piezoelectric actuator 4, a first root platform simulator 5, and a first simulator holder 6. Wherein, a first sliding chute 7 (which can be a horizontal sliding chute) is arranged on the movable flat plate 1, and is connected on the bottom plate by bolts, and the relative motion direction of the blade root platform simulation pieces at two sides can be changed by adjusting the connecting position; a piezoelectric actuator 4 is mounted between the piezoelectric holding device 2 and the motion transmitting mechanism 3 for generating a desired sinusoidal simple harmonic displacement signal; the piezoelectric holding device 2 is used for ensuring that the direction of the displacement signal input by the piezoelectric actuator 4 is single and stable, and transmitting the displacement signal to the first blade root platform simulation piece 5; the motion transmitting mechanism 3 is used for ensuring that the magnitude of the displacement signal input by the piezoelectric actuator 4 is accurate and lossless and transmitting the displacement signal to the first blade root platform simulation piece 5; the piezoelectric holding device 2 and the motion transmitting mechanism 3 are both provided with a second chute 8 which can be connected to the movable flat plate 1 through bolts; the first simulation clamp 6 is rigidly connected to the motion transfer mechanism 3 and clamps the first root platform simulation 5 with bolts to ensure accurate transmission of input displacement information.
The first root platform simulator 5 is provided with a set of contact rails 17 for axial face-to-face contact with the friction damper for converting medium pressure loads into high pressure loads on the friction damper contact plane.
The signal measuring module comprises a fixing flat plate 9, a signal holding device 10, a piezoelectric force sensor 11, a force transmission mechanism 12, a second blade root platform simulation piece 13, a second simulation piece clamp 14 and a laser vibration meter 15. Wherein, the fixed flat plate 9 is installed and positioned on the bottom plate through a bottom bolt; the signal holding device 10 is arranged on the fixed flat plate 9 through a bolt and is vertically and rigidly connected with the piezoelectric force sensor 11, so that a single and stable mechanical signal in the output direction is ensured; the force transmission mechanism 12 is two mutually perpendicular hollow geometric bodies with two elongated sides, is rigid in the axial direction and can be regarded as flexible in the transverse direction (the axial rigidity ratio to the transverse rigidity >100), and is respectively connected with the two piezoelectric force sensors 11 to ensure the accurate transmission of output mechanical information; the piezoelectric force sensor 11 has a sufficient load range and a small signal loss, receives a mechanical signal of the second blade root platform simulator 13, and outputs the result. The second blade root platform simulator 13 is provided with a set of contact rails 17 for axial positioning contact with the friction damper. Optionally, the second simulation piece clamp 14 is integrated with the force transmission mechanism 12, and clamps the second blade root platform simulation piece 13 through a bolt, so as to ensure lossless transmission of output mechanical information; the laser vibration meter 15 is installed perpendicular to the experimental system platform, and the emitted laser respectively and vertically irradiates the position of the contact area on the contact surface of the damper simulation piece.
The friction damper 16 is a semi-cylinder, and is in surface-to-surface contact and line-to-surface contact with the dummy members on both sides, respectively. The friction damper 16 is connected to the wire 18 in a vertical direction, and simulates a centrifugal force load by applying a static load.
In the embodiment of the invention, the displacement of the in-plane friction damper corresponding to the bending modes of the blades in the same phase (relative motion in the y direction between the platforms) and in the different phase (relative motion in the x direction) can be realized by changing the installation position of the motion generation module.
In the embodiment of the invention, all parts of the motion generation module can be flexibly installed, moved and positioned through the design of the bidirectional sliding groove. The motion transmission mechanism transmits motion information without introducing noise components, and protects the transmission signal from being interfered by a bad load. The blade root platform simulation pieces on the two sides can be processed by using various high-temperature alloy steel materials commonly used by the gas turbine and processed into different contact angles so as to research the influence of different materials and processing angles on the frictional contact characteristic of the blade root platform and the damper. For example, the friction damper can be processed into a cylinder, a semi-cylinder, a sphere and other geometric forms, and forms a plurality of contact forms such as point-surface, line-surface, surface-surface and the like with the blade root platform simulation parts on two sides so as to research the influence of different contact states on the blade root platform-friction damping characteristics.
In the embodiment of the invention, the force transmitting mechanism is two elongated geometric bodies on two sides which are perpendicular to each other, the mechanical signal is decomposed into a normal signal and a transverse signal, and the normal direction rigidity of the force transmitting mechanism is far greater than the transverse rigidity, so that the normal positive pressure signal is captured by the force sensor, and the interference of other components is avoided. The piezoelectric force sensor has enough load range and small signal loss, and can keep good signal capture capability in a high-frequency range.
In the embodiment of the invention, the normal force signals are decomposed along the x direction and the y direction, so that a friction hysteresis loop of in-phase (out-of-phase) relative motion between blade root platforms at two sides can be obtained. And decomposing the friction damper along the directions of the contact surfaces at the two sides to obtain a friction hysteresis loop of the relative motion of the contact surfaces between the blade root platform and the friction damper. The conditions of excitation frequency, contact surface material, centrifugal load, input displacement and the like are changed, and the corresponding friction hysteresis loop can be measured under different input conditions. The friction hysteresis loop is analyzed to obtain characteristic parameters such as tangential contact stiffness coefficient, material friction coefficient, equivalent stiffness coefficient, equivalent damping coefficient and the like which reflect the motion characteristics of the contact surface, a friction contact characteristic parameter database is formed, and the linear equivalence and quantitative evaluation of the friction contact characteristics are realized.
In the system of the embodiment of the invention, the piezoelectric actuator, the piezoelectric sensor and the laser vibration meter are respectively used as a signal generating device, a signal receiving device and a signal measuring device, so that the high-precision generation and collection of an experimental millimeter-level displacement signal and a mechanical signal can be ensured; the piezoelectric holding device, the signal holding device, the motion transmitting mechanism and the force transmitting mechanism are adopted, so that the nondestructive and stable transmission of the experiment signal can be ensured. The invention directly measures and collects the displacement and force signals on the contact surface of the blade root platform and the damper, thereby better knowing the motion characteristic of the friction damper, obtaining the friction hysteresis loop, the friction coefficient, the tangential contact stiffness coefficient, the equivalent friction coefficient, the equivalent damping coefficient and other contact parameters, and realizing the double targets of direct experimental research and contact parameter estimation.
Description of the parameters: y isLP-yRP-relative movement displacement of the blade root platforms on both sides in the y-direction, xLP-xRP-relative movement displacement of the blade root platforms on both sides in the x-direction, dlp、drpDisplacement of the left and right blade root platform simulator contact surfaces with the friction damper, θLP、θRP-left and right blade root platform simulator angles, FCCentrifugal force load, FL-a first root platform simulator normal force, FRSecond blade root platform simulator normal force, FRv-a second blade root platform simulation element normal force y-direction component, FRh-a second leaf root platform simulation element x-direction component, uLD-uLPFirst blade root platform and friction damper contact surface relative displacement, uRD-uRP-the second blade root platform is displaced relative to the friction damper interface; t isDL-a first root platform simulator interface friction with the friction damper; t isDR-a second blade root platform simulator interface friction with the friction damper; k is a radical ofd、kd1、kd2-a tangential contact stiffness coefficient; f. ofm、f′m、f″m-absolute value of friction; n-positive pressure loading; mu, muL、μR-a coefficient of friction; keq-coefficient of equivalent stiffness between the frictionally engaged surfaces; ceq-an equivalent damping coefficient between the frictionally engaged surfaces; f (T, theta) -hysteresis loop of friction, Tm-the relative displacement amplitude corresponding to the hysteresis loop.
Referring to fig. 3, in the embodiment of the present invention, by changing the installation position of the motion generating module, the displacement motion of the in-plane friction damper corresponding to the bending mode of the blade in the same phase (the y-direction relative motion between the platforms) can be realized. When the piezoelectric actuator 4 generates a relative motion signal in the y direction, as shown in the system layout mode of fig. 3(a), the relative motion signal is transmitted to the blade root platform through the motion transmission mechanism 3, and the blade root platform simulation pieces on two sides generate a relative motion displacement y in the y directionLP-yRPAs shown in fig. 3(b), the displacements d of the contact surfaces of the blade root platform simulation parts and the friction damper at two sides are obtained according to the vector decomposition principlelpAnd drpAs shown in FIG. 3(c), the in-phase relative displacement of the adjacent root platform contact surfaces at this time can simulate the in-phase motion of the gas turbine blade in bending vibration during actual operation.
Referring to fig. 4, the system layout shown in fig. 4(a) is obtained by rotating the motion generation module of fig. 3 by 90 degrees, which can achieve the displacement motion of the in-plane friction damper corresponding to the blade bending mode out of phase (relative motion in x-direction). In the system layout mode shown in fig. 4(a), when the piezoelectric actuator 4 generates a relative motion signal in the horizontal direction, the relative motion signal is transmitted to the blade root platform through the motion transmission mechanism 3, and the blade root platform simulation pieces on two sides generate a relative motion displacement x in the horizontal directionLP-xRPSimilarly, as shown in fig. 4(b), the displacements of the contact surfaces of the blade root platform simulation members at two sides and the friction damper are respectively d according to the vector decomposition principlelpAnd drpAs shown in FIG. 4(c), the out-of-phase relative displacement of the adjacent root platform contact surfaces at this time may simulate the out-of-phase behavior of the gas turbine blade in bending oscillations during actual operation. And because each part of the motion generation module is arranged on the bottom plate with the bolt holes through the design of the bidirectional sliding grooves in the x direction and the y direction, the movement and the transformation of the arrangement mode can be flexibly realized.
Referring to fig. 5, in the embodiment of the present invention, the blade root platform simulation components on both sides are respectively provided with a group of contact rails, an axial positioning contact surface is established with the friction damper, a medium-pressure load can be converted into a high-pressure load on a contact plane of the friction damper, and a specific distribution area of the contact pressure can be determined according to a control length trace and a wear trace on the contact surface of the rails.
Referring to fig. 6, a schematic diagram of various types of friction dampers in cooperation with a blade root platform is shown in an embodiment of the present invention. When the angles of both sides of the blade root platform are the same (theta)LP＝θRP) The friction damper can be selected as a sphere or a cylinder, and forms point-surface contact or line-surface contact with both sides, as shown in fig. 6 (a); alternatively, a single-sided half cylinder may be used to make line-surface contact and surface-surface contact with both sides, respectively, as shown in fig. 6 (b). When the angles of the two sides of the platform are different (theta)LP≠θRP) The friction damper can be selected as a unilateral semi-cylinder, which forms a line-surface contact and a surface-surface contact with both sides, respectively, as shown in fig. 6 (c); or two-sided semi-cylinders which are in surface-to-surface contact with both sides,as shown in fig. 6 (d). By changing the geometric form of the friction damper and the molded line angle of the corresponding blade root platform, the measurement and research of the friction damping characteristics of different contact angles and contact characteristics can be carried out.
Referring to fig. 7, in the embodiment of the present invention, a blade root platform simulation is selected as a research object, and a friction hysteresis loop of the in-phase (out-of-phase) relative motion between blade root platforms on two sides is shown. As shown in fig. 7(a), from the known quantity F by force analysisCAnd a measured quantity FRSolving to obtain a tangential force F of the first blade root platform simulation pieceL. As shown in fig. 7(b), the piezoelectric actuator can generate the displacement x by different arrangements as shown in fig. 3 and 4LP-xRPAnd yLP-yRP(ii) a Meanwhile, the normal force F of the second blade root platform simulation element directly measured by the piezoelectric force sensor is obtainedRThe component F can be obtained by decomposition in the y and x directionsRvAnd component FRh. As shown in FIG. 7(c), F was obtainedRv(FRh) Relative displacement y along with blade root platforms on two sidesLP-yRP(xLP-xRP) I.e. the friction hysteresis loop of the in-phase (out-of-phase) relative motion between the blade root platforms on both sides.
Referring to fig. 8, in the embodiment of the present invention, the friction contact surface is selected as the research object, and a friction hysteresis loop of the relative motion between the contact surfaces is shown. As shown in fig. 8(a), from the known quantity F by force analysisCSolving the angle of the contact surface to obtain the friction force T of the contact surfaces on two sidesDLAnd TDR. As shown in FIG. 8(b), the displacement u of the contact surfaces on both sides can be measured by the laser vibration meter 15LD-uLPAnd uRD-uRP. As shown in FIG. 8(c), T can be obtainedDL(TDR) Relative displacement u between friction damper and blade root platformLD-uLP(uRD-uRP) I.e. the respective friction hysteresis loops of the contact surfaces on both sides.
In the embodiment of the present invention, the slope of the initial stage of the micro-motion slip in the initial loading and unloading process in the hysteresis curve measured in fig. 8(b) is averaged, so as to calculate the corresponding tangential contact stiffness coefficient:
kd＝(kd1+kd2)/2，
according to a hysteresis curve obtained by experimental measurement, positive and negative absolute values f 'of friction force in the integral macroscopic sliding stage in the curve'mAnd f ″)mTaking and averaging to obtain fmAnd then dividing the positive pressure load N by the corresponding positive pressure load N to calculate the friction coefficient mu, namely:
when calculating the coefficient of friction mu of the first root platform contact surfaceLWhen N is equal to FL(ii) a When calculating the friction coefficient mu of the contact surface of the second blade root platformRWhen N is equal to FR。
According to the linearization criterion, the friction contact surface is simplified into a no-mass spring damping system, and the friction force between the contact surfaces can be calculated by the superposition of the elastic force and the damping force, namely:
wherein, KeqIs the equivalent stiffness coefficient between the friction contact surfaces, CeqIs the equivalent damping coefficient between the friction contact surfaces. According to the energy dissipation principle, the friction dissipation energy is the area surrounded by the hysteresis loop, so that the equivalent stiffness coefficient K between the friction contact surfaces can be obtained by calculating the surface integral of the friction hysteresis loopeqAnd equivalent damping coefficient Ceq：
Wherein f (T, θ) represents a friction hysteresis loop, TmRelative displacement amplitude, K, corresponding to the hysteresis loopeqCoefficient of equivalent stiffness between the frictionally engaged surfaces, CeqThe equivalent damping coefficient between the friction contact surfaces.
Parameters such as contact surface material, applied centrifugal load, input displacement of the piezoelectric brake and the like are changed, different friction hysteresis loops are measured, the contact state of the friction damper is judged, tangential contact stiffness coefficients, material friction coefficients, equivalent stiffness coefficients and equivalent damping coefficients under different input conditions are obtained according to the analysis, and a database of friction contact characteristic parameters applicable to engineering is formed.
Referring to fig. 9, a method for testing the dry friction damping dynamic characteristics of the gas turbine blade material according to the embodiment of the present invention includes the following steps:
firstly, a stable and lossless sine simple harmonic displacement signal is generated by the motion generation module according to different arrangement modes, is accurately transmitted to the friction damper, is transmitted to the signal measurement module through the action of the contact surface of the blade root platforms on two sides, and outputs a normal mechanical signal with a single and stable direction.
And measuring friction hysteresis loops corresponding to different contact surface materials, centrifugal loads, input displacements and the like according to the input and output signals, processing data to obtain characteristic parameters reflecting the motion characteristics of the contact surfaces, such as a tangential contact stiffness coefficient, a material friction coefficient, an equivalent stiffness coefficient, an equivalent damping coefficient and the like, establishing a friction contact characteristic parameter database, and realizing linear equivalent and quantitative evaluation of the dry friction damping dynamic characteristics of the blade material.
For example, given measured data parameters for a set of operating conditions in a database of frictional contact characteristic parameters for a particular centrifugal load:
for the same-phase relative motion, when the relative displacement measurement interval is 0-6 mu m, the linear calculation formula of the corresponding tangential contact stiffness coefficient, material friction coefficient, equivalent stiffness coefficient and equivalent damping coefficient in the database is as follows:
tangential contact stiffness coefficient:
coefficient of friction of the material:
equivalent stiffness coefficient:
equivalent damping coefficient:
for out-of-phase relative motion, the linear calculation formula of the tangential contact stiffness coefficient, the material friction coefficient, the equivalent stiffness coefficient and the equivalent damping coefficient in the database is as follows when the relative displacement interval is measured to be 0-6 mu m by using the friction damper material 1Cr 13:
tangential contact stiffness coefficient:
coefficient of friction of the material:
equivalent stiffness coefficient:
equivalent damping coefficient:
in engineering application, if the motion characteristic of the blade made of the high-temperature nickel-based alloy material when the contact surface relative displacement is 1 mu m in the same-phase motion is required to be obtained, the tangential contact stiffness coefficient at the moment is 260618.4N m only by substituting the input displacement 1 mu m into a database for calculation-1The coefficient of friction of the material is 0.28783, and the equivalent stiffness coefficient is 117559.2 N.m-1The equivalent damping coefficient is 247433.2N · s-1·m-1The contact surface can be quickly judged to be in a viscous state according to the contact parameters; if the movement characteristic of the blade made of the high-temperature nickel-based alloy material when the relative displacement of the contact surface is 3 mu m during the out-of-phase movement is required to be obtainedAnd the tangential contact stiffness coefficient at the moment is 258399.2N m only by substituting the input displacement of 3 mu m into the database-1The coefficient of friction of the material is 0.26536, and the equivalent stiffness coefficient is 349098.0 N.m-1The equivalent damping coefficient is 89559.4N · s-1·m-1The contact surface is in a micro-motion sliding state. And the modal and harmonic response analysis can be further carried out on the blade by substituting the contact parameters into the numerical analysis model.
The core innovation points of the invention comprise: the friction characteristics of the aviation material are not studied, so that the test system provided by the embodiment of the invention can realize accurate measurement of the characteristic parameters of the dry friction damping contact surface of the gas turbine blade material, and can analyze the influence of the change of input conditions such as excitation frequency, contact pressure, geometric shape, centrifugal load, motion direction and the like on the contact state; secondly, specifically, the complex nonlinear problem of frictional contact is converted into equivalent linear parameters for quantitative evaluation, the combination of direct experimental study and contact parameter estimation is realized, and the dynamic characteristics of dry friction damping of the gas turbine blade material are revealed; and thirdly, universality is realized, a frictional contact characteristic parameter database suitable for engineering technology is formed, and the frictional contact characteristic parameter database is convenient to directly obtain and apply on engineering.
The invention discloses a system for testing the dynamic characteristics of dry friction damping of a gas turbine blade material, wherein a motion generation module generates stable and lossless sine simple harmonic displacement signals according to different arrangement modes, the stable and lossless sine simple harmonic displacement signals are accurately transmitted to a friction damper and transmitted to a signal measurement module through the action of contact surfaces of blade root platforms at two sides, normal mechanical signals with single and stable direction are output, corresponding friction hysteresis loops under the conditions of different excitation frequencies, contact surface materials, centrifugal loads, input displacement and the like are obtained according to input and output signals, and data processing is carried out to obtain characteristic parameters reflecting the motion characteristics of the contact surfaces, such as a tangential contact stiffness coefficient, a material friction coefficient, an equivalent stiffness coefficient, an equivalent damping coefficient and the like.
The invention can realize the accurate measurement of the characteristic parameters of the dry friction damping contact surface of the material, analyze the influence of the input condition changes such as excitation frequency, contact pressure, geometric shape, centrifugal load, motion direction and the like on the contact state, convert the complex nonlinear problem of friction contact into equivalent linear parameters for quantitative evaluation, realize the combination of direct experimental study and contact parameter estimation, reveal the dynamic characteristics of the dry friction damping of the material of the gas turbine blade, form a friction contact characteristic parameter database suitable for engineering technology and provide important reference for the design and application of the gas turbine blade friction damper.
Although the present invention has been described in detail with reference to the above embodiments, those skilled in the art can make modifications and equivalents to the embodiments of the present invention without departing from the spirit and scope of the present invention, which is set forth in the claims of the present application.
Claims (10)
1. An experimental test system for dry friction damping dynamics, comprising:
a mobile plate (1) for detachable fixed mounting on a predetermined base plate or base; the piezoelectric holding device (2) and the motion transmission mechanism (3) are fixedly arranged on the movable flat plate (1); the piezoelectric holding device (2) and the motion transmission mechanism (3) are connected through a piezoelectric actuator (4); the motion transmitting mechanism (3) is fixedly provided with a first simulation piece clamp (6); a first root platform simulation piece (5) is arranged on the first simulation piece clamp (6); wherein the first root platform simulator (5) is provided with a contact surface for contacting a friction damper;
a fixing plate (9) for fixing and mounting on a predetermined bottom plate or base; the fixed flat plate (9) is fixedly provided with a signal holding device (10); the signal holding device (10) is provided with a pressure power sensor (11); the piezoelectric force sensor (11) is connected with a second simulation piece clamp (14) through a force transmitting mechanism (12), and a second blade root platform simulation piece (13) is installed on the second simulation piece clamp (14); wherein the second root platform simulator (13) is provided with a contact surface for contacting a friction damper;
the static load simulation device is used for applying centrifugal force load to the friction damper;
and the laser vibration meter (15) is used for measuring the contact area of the first blade root platform simulation piece (5) and the friction damper and the displacement of the contact area of the second blade root platform simulation piece (13) and the friction damper.
2. An experimental test system for dry friction damping dynamics according to claim 1 characterized in that contact tracks (17) are provided on the contact surfaces of the first and second root platform simulator (5, 13).
3. The system for experimental testing of the dynamic characteristics of dry friction damping according to claim 1, characterized in that the moving plate (1), the piezoelectric holding device (2) and the motion transmission mechanism (3) are provided with mounting chutes.
4. An experimental test system of dry friction damping dynamics in accordance with claim 1 characterized by that the force transmission mechanism (12) is two hollow geometric bodies perpendicular to each other, rigid in the axial direction and flexible in the transverse direction.
5. The system for experimental testing of dry friction damping dynamics of claim 1 further comprising:
a friction damper (16), the friction damper (16) being a sphere, a cylinder, a single sided semi-cylinder, or a double sided semi-cylinder.
6. Experimental test system for dry friction damping dynamics according to claim 5, characterized in that the contact form of the first root platform simulator (5) with the friction damper (16) and the second root platform simulator (13) with the friction damper (16) is point-to-face, line-to-face or face-to-face.
7. The experimental test system for the dynamic characteristics of dry friction damping according to claim 5, characterized in that the laser emitted by the laser vibrometer (15) is perpendicularly irradiated onto the contact areas of the first root platform simulator (5) and the friction damper (16) and the second root platform simulator (13) and the friction damper (16), respectively.
8. An experimental test method for dynamic characteristics of dry friction damping, which is based on the experimental test system of claim 1, and comprises the following steps:
according to the plane rectangular coordinate, the vertical direction is the y-axis direction, and the horizontal direction is the x-axis direction; adjusting the relative installation positions of the movable flat plate and the fixed flat plate to enable the piezoelectric actuator to output sinusoidal simple harmonic displacement signals in the vertical direction or the horizontal direction, enabling the force transmission mechanism to decompose received mechanical signals into normal positive pressure signals and horizontal direction signals, and enabling the piezoelectric force sensor to acquire the normal positive pressure signals;
obtaining corresponding friction hysteresis loops under the conditions of different preset contact surface materials, centrifugal loads and input displacement;
obtaining characteristic parameters reflecting the motion characteristics of the contact surface based on the obtained friction hysteresis loop;
establishing a frictional contact characteristic parameter database based on the characteristic parameters; and linear equivalence and quantitative evaluation of the dynamic characteristics of the dry friction damping are realized based on the frictional contact characteristic parameter database.
9. The method for experimental testing of the dynamic characteristics of dry friction damping according to claim 8, wherein the characteristic parameters reflecting the motion characteristics of the contact surface comprise: tangential contact stiffness coefficient, material friction coefficient, equivalent stiffness coefficient and equivalent damping coefficient;
wherein, the tangential contact rigidity coefficient calculation expression is as follows:
kd＝(kd1+kd2)/2，
in the formula, kdIs a tangential connectionCoefficient of touch stiffness, kd1For measuring the slope, k, of the initial stage of micromotion slip during loading in the hysteresis curved2The slope of the initial stage of the micro-motion slip in the unloading process in the hysteresis curve obtained by measurement;
according to the friction hysteresis loop obtained by experimental measurement, the positive and negative absolute values f 'of the friction force in the integral macroscopic sliding stage'mAnd
taking and averaging to obtain fmAnd then dividing the obtained value by the corresponding positive pressure load N to obtain a material friction coefficient mu, wherein the expression is as follows:
calculating the coefficient of friction mu of the contact surface of the first root platform simulatorLWhen N is equal to FL(ii) a When calculating the coefficient of friction mu of the contact surface of the second leaf root platform simulationRWhen N is equal to FR(ii) a Wherein, FLSimulating a member normal force for the first root platform, FRSimulating a normal force for the second leaf root platform;
according to the linearization criterion, the contact surface is simplified into a no-mass spring damping system, the friction force between the contact surfaces is calculated by the superposition of the elastic force and the damping force, and the expression is as follows:
wherein, KeqIs the equivalent stiffness coefficient between the friction contact surfaces, CeqF is the friction force between the contact surfaces, and u is the relative displacement between the contact surfaces;
according to the energy dissipation principle, friction dissipation energy is the area surrounded by the hysteresis loop, and the friction hysteresis loop is subjected to surface integration to obtain the equivalent stiffness coefficient K between the friction contact surfaceseqAnd equivalent damping systemNumber CeqThe expressions are respectively:
wherein f (T, θ) represents a friction hysteresis loop, TmThe relative displacement amplitude corresponding to the hysteresis loop.
10. The experimental test method for the dry friction damping dynamic characteristics according to claim 8, is used for the experimental test of the dry friction damping dynamic characteristics of the high-temperature nickel-based alloy material of the gas turbine blade.
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Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102156035A (en) * | 2011-03-24 | 2011-08-17 | 西安交通大学 | Turbine blade vibration characteristic testing and measuring device with shroud damping block and blade root wedged damping block |
| CN105156155A (en) * | 2015-07-06 | 2015-12-16 | 西安交通大学 | Vibration reducing and pressure bearing damping structure for blade root platform of movable blades |
| CN106528982A (en) * | 2016-10-26 | 2017-03-22 | 西安交通大学 | Vibration analysis method for dry frictional damping mistuned blades with tendons and shroud bands |
| CN111832200A (en) * | 2020-06-04 | 2020-10-27 | 台州学院 | Frequency response analysis method for circularly symmetric structure of additional dry friction damper |
| CN112665844A (en) * | 2020-12-25 | 2021-04-16 | 南京航空航天大学 | System and method for testing high-frequency vibration reduction characteristics of turbine blade with friction damping device |
| CN112697366A (en) * | 2020-12-09 | 2021-04-23 | 西安交通大学 | Beam-damper vibration characteristic measurement experimental device and method considering non-harmonious tuning |
| CN113177273A (en) * | 2021-04-19 | 2021-07-27 | 西安交通大学 | Gas turbine compressor and turbine blade contact rigidity and damping analysis solving method |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7398669B2 (en) * | 2005-09-28 | 2008-07-15 | Material Sciences Corporation | Test apparatus and method of measuring surface friction of a brake pad insulator material and method of use of a brake dynamometer |
-
2021
- 2021-07-30 CN CN202110876086.4A patent/CN113720768B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102156035A (en) * | 2011-03-24 | 2011-08-17 | 西安交通大学 | Turbine blade vibration characteristic testing and measuring device with shroud damping block and blade root wedged damping block |
| CN105156155A (en) * | 2015-07-06 | 2015-12-16 | 西安交通大学 | Vibration reducing and pressure bearing damping structure for blade root platform of movable blades |
| CN106528982A (en) * | 2016-10-26 | 2017-03-22 | 西安交通大学 | Vibration analysis method for dry frictional damping mistuned blades with tendons and shroud bands |
| CN111832200A (en) * | 2020-06-04 | 2020-10-27 | 台州学院 | Frequency response analysis method for circularly symmetric structure of additional dry friction damper |
| CN112697366A (en) * | 2020-12-09 | 2021-04-23 | 西安交通大学 | Beam-damper vibration characteristic measurement experimental device and method considering non-harmonious tuning |
| CN112665844A (en) * | 2020-12-25 | 2021-04-16 | 南京航空航天大学 | System and method for testing high-frequency vibration reduction characteristics of turbine blade with friction damping device |
| CN113177273A (en) * | 2021-04-19 | 2021-07-27 | 西安交通大学 | Gas turbine compressor and turbine blade contact rigidity and damping analysis solving method |
Non-Patent Citations (2)
| Title |
|---|
| 整体围带叶片干摩擦阻尼振动特性实验研究;吴君等;《中国电机工程学报》;20101230;第110-116页 * |
| 新型阻尼结构叶片振动特性试验研究;周显丁等;《东方汽轮机》;20111231(第04期);第4-10页 * |
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