CN115235774A - Device and method for measuring axial dynamic load of blade - Google Patents
Device and method for measuring axial dynamic load of blade Download PDFInfo
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- CN115235774A CN115235774A CN202210835920.XA CN202210835920A CN115235774A CN 115235774 A CN115235774 A CN 115235774A CN 202210835920 A CN202210835920 A CN 202210835920A CN 115235774 A CN115235774 A CN 115235774A
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- 238000000034 method Methods 0.000 title claims abstract description 43
- 210000000078 claw Anatomy 0.000 claims abstract description 104
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- 238000005259 measurement Methods 0.000 claims description 41
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- 230000008569 process Effects 0.000 claims description 17
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- 238000009864 tensile test Methods 0.000 description 7
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- 238000007906 compression Methods 0.000 description 3
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- 238000012545 processing Methods 0.000 description 3
- 229910001069 Ti alloy Inorganic materials 0.000 description 2
- 230000009471 action Effects 0.000 description 2
- 239000000956 alloy Substances 0.000 description 2
- 238000007405 data analysis Methods 0.000 description 2
- WABPQHHGFIMREM-UHFFFAOYSA-N lead(0) Chemical compound [Pb] WABPQHHGFIMREM-UHFFFAOYSA-N 0.000 description 2
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- 238000012544 monitoring process Methods 0.000 description 2
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- 230000003247 decreasing effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M15/00—Testing of engines
- G01M15/02—Details or accessories of testing apparatus
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
- G01L5/00—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
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Abstract
The invention discloses a device and a method for measuring axial dynamic load of a blade, and belongs to the field of turbine engines. The device comprises a closed test cavity, a rotating speed-increasing system, a load measuring tool and a data acquisition system; the rotary speed increasing system is arranged on a cavity cover of the closed test cavity; the load measuring tool is positioned in the closed test cavity and is connected with the rotary speed increasing system; the data acquisition system is used for acquiring test data; the load measuring tool comprises a tool mandrel, a wheel disc, blades, a force measuring claw disc and a pressing device, wherein the top of the tool mandrel is connected with a power output end of a rotating speed increasing system, the wheel disc and the force measuring claw disc are fixed on the tool mandrel through the pressing device, the wheel disc is positioned above the force measuring claw disc, and the blades are installed in a mortise of the wheel disc; and strain gauges are arranged on the force measuring claw disc and the tooling mandrel and are respectively used for measuring the axial dynamic load of a single blade and the integral axial dynamic load of all blades. The measuring working condition is close to the real working state, and the data reliability is high.
Description
Technical Field
The invention belongs to the field of turbomachinery, and relates to a device and a method for measuring axial dynamic load of a blade, which are used for the related technical fields of design, test, processing and application of a fan and an air compressor of a turbine engine.
Background
The turbine engine compressor is formed by installing a wheel disc and blades together through a tongue-and-groove structure, compresses air through high-speed rotation and provides high-pressure air for a hot end acting part. The typical gas compressor wheel disc mortise and a shaft system form a certain angle, when a blade is installed in the mortise and rotates at a high speed, the mortise part bears the combined action of centrifugal load and axial dynamic load, and the axial dynamic load is generally borne by a pin, a baffle plate and other structures, so that the blade is prevented from axially sliding. Therefore, the method for accurately obtaining the axial dynamic load of the compressor blade in the rotating state has important significance for the design and optimization of structures such as pins, baffles and the like.
At present, methods for acquiring axial loads of compressor blades of turbine engines comprise methods such as a finite element calculation method and a static tensile test method, but the methods have the following problems: 1) The axial load of the blade is the component force of the centrifugal load of the blade in the axial direction, and under the condition of certain structure and angle of the mortise, the size of the axial load is related to the centrifugal load of the blade and the friction coefficient of the contact surface of the mortise. Different types of lubricants are usually coated on the mortise part of the actual compressor, and the friction coefficient of the lubricants cannot be accurately obtained, so that the actual axial dynamic load cannot be accurately calculated by the finite element method. In addition, the finite element method calculation result is related to the grid size, the boundary condition setting, and the like, and the calculation result needs further verification. 2) The static tensile test method can coat a lubricant which is consistent with the real working state in the mortise, but the static tensile test method is difficult to completely reproduce the centrifugal stress state of the high-speed rotation of the blade, and the static friction coefficient and the rotation state have a certain difference, so that the reliability of the test result of the static tensile test method is poor, and the axial dynamic load characteristic of the rotation state cannot be reflected. In conclusion, the existing finite element method and static tensile test method have defects in the aspect of accurate calculation and measurement of axial dynamic load of the compressor blade.
Therefore, a device and a method for measuring the axial dynamic load of the compressor blade of the turbine engine are needed urgently, the requirements of the true high-speed rotation state and the mortise lubrication state of the blade are met, the device and the method have the characteristics of simplicity and convenience in test method, high accuracy, good applicability of a test object and the like, and the problems that the conventional finite element calculation cannot be carried out, the credibility is low, and a static tensile test cannot simulate the true rotation state are solved, so that the axial dynamic load of the compressor blade is measured closer to the engine state, the measurement result is more accurate, and the device and the method are used for structural design and optimization of the blade joggle joint part.
Disclosure of Invention
The invention provides a device and a method for measuring axial dynamic load of an engine blade, aiming at the problem that the axial dynamic load of the existing turbine engine compressor blade is difficult to accurately measure, meeting the requirements that the blade keeps rotating at high speed and the friction state of a mortise is consistent with the real working condition in the measuring process, having the characteristics of high testing efficiency, accurate testing result, wide applicable compressor model range and the like, solving the problems that the existing finite element calculation method and static tensile test method have poor calculation reliability and can not simulate the real rotating working state, leading the axial dynamic load measurement of the blade to be closer to the working state of the engine, and providing more accurate and reliable test data for the structural design and optimization of the engine.
In order to solve the technical problem, the solution of the invention is as follows:
a turbine engine compressor blade axial dynamic load measuring device is used for measuring axial dynamic load of a compressor joggle assembly blade and axial load of other rotor part joggle assembly blades, and comprises a closed test cavity, a rotating speed-increasing system, a load measuring tool and a data acquisition system; the rotary speed increasing system is arranged on a cavity cover of the closed test cavity; the load measuring tool is positioned in the closed test cavity and is connected with the rotating speed increasing system; the data acquisition system is used for acquiring test data;
the load measuring tool comprises a tool mandrel, a wheel disc, blades, a force measuring claw disc and a pressing device, wherein the top of the tool mandrel is connected with a power output end of a rotating speed increasing system, the wheel disc and the force measuring claw disc are fixed on the tool mandrel through the pressing device, the wheel disc is positioned on the force measuring claw disc, and the blades are arranged in a mortise of the wheel disc;
and the force measuring claw disc and the tooling mandrel are provided with strain gauges which are respectively used for measuring the axial dynamic load of a single blade and the integral axial dynamic load of all blades. Preferably, the closed test cavity is defined by a cavity cover and a cavity wall and is used for placing a blade rotor with a measuring compressor in the closed test cavity, the closed test cavity has a vacuumizing function and a safety protection function, the rotation resistance of the blade is reduced, the rotor is enabled to reach a high-speed rotation state, and safety accidents caused by the flying-off of the blade are prevented;
the rotary speed-increasing system is connected with a motor, a driving main shaft in the speed-increasing system penetrates through a cavity cover to extend into a test cavity and is used for connecting a test tool and driving a blade rotor of an air compressor to rotate, the driving main shaft is of a central through hole structure and is used for being connected with a strain measurement lead in a penetrating manner during testing, and a high-speed electric slip ring is mounted at the upper end of the driving main shaft and is used for connecting the strain measurement lead rotating at high speed on the driving main shaft with an external static measurement lead;
the load measuring tool comprises a mandrel, a gas compressor, blades, an upper gland, a lower gland, a force measuring claw disc, a locking nut and the like, wherein the top of the mandrel is connected with a driving main shaft, the blades are installed on the gas compressor and then are integrally installed on the mandrel through the upper gland, the lower gland and the locking nut, the force measuring claw disc is also installed on the mandrel through the locking nut, and a wheel disc rim of the force measuring claw disc is provided with a force measuring claw which is tightly attached to a blade rotor of the gas compressor and is used for measuring the axial load of a single blade; the mandrel is provided with a force measuring pull rod section with a smaller diameter and used for measuring the integral axial load on the mandrel; the mandrel is of a central through hole structure and is used for penetrating and connecting a measurement lead.
The data acquisition system comprises a strain gauge, a dynamic and static strain gauge, a measuring lead, a vibration sensor, a rotating speed controller and a computer, wherein the strain gauge is adhered to a measuring pull rod section of a mandrel and a flower claw on a rim of a force measuring claw disc, the strain gauge is connected with the measuring lead, the measuring lead is connected to the external dynamic and static strain gauge sequentially through a central through hole of the mandrel, a central through hole of a driving main shaft and a high-speed electric slip ring, the vibration sensor and the rotating speed sensor are arranged in a speed increasing system and used for measuring the vibration and the rotating speed of the main shaft and transmitting data to the speed increasing system controller, the speed increasing system controller is used for processing rotating speed signals and controlling the rotating speed of a rotor in real time to meet the requirement of test parameters, and the rotating speed signals and the strain signals are finally input to the computer for real-time analysis and display;
the measuring range of the strain gauge is at least not less than 2%;
the upper gland and the force measuring claw disc comprise threaded holes, and are used for performing dynamic balance correction by increasing and decreasing nuts before a blade axial dynamic load rotation measurement test;
as the optimization of the invention, the force measuring claw disk should be made of a material with high strength, good toughness and wide temperature use range, and preferably made of a high-temperature alloy material;
preferably, the mandrel is made of a material with high strength and low elastic modulus, and preferably a titanium alloy material;
preferably, the tooling mandrel comprises a connecting section, a first boss section, a second boss section and an auxiliary section which are connected in sequence; the connecting section is used for connecting a power output end of the rotary speed increasing system, the first boss section is used for positioning the wheel disc, and the second boss section is used for positioning the force measuring claw disc; and a force measuring pull rod section with a smaller diameter is also arranged on the second boss section.
The first boss section and the second boss section are provided with local thread sections, a second matching surface for mounting the force measuring claw disc is arranged behind the local thread section of the first boss section and in front of the local thread section of the second boss section, the second matching surface is matched with the inner wall of a central through hole of the force measuring claw disc, and the force measuring pull rod section is positioned in the central through hole of the force measuring claw disc; a first matching surface used for installing the wheel disc is arranged in front of the local thread section of the first boss section, and the first matching surface is matched with the inner wall of the central through hole of the wheel disc.
The invention has the following beneficial effects:
1) The invention designs a device for measuring the axial dynamic load of the blades of the compressor, which can detect the change condition of the load along with the rotating speed in the high-speed rotating process of a plurality of blades in real time, realizes the aim of accurately measuring the axial dynamic load of the blades of the compressor of a turbine engine under the real rotating state and the lubricating condition, greatly improves the measurement reliability and the measurement precision of the axial dynamic load of the blades of the compressor, improves the blade load measurement efficiency, and overcomes the problem that the traditional finite element method calculation and the static test measurement method are difficult to realize.
Specifically, the invention designs a mandrel with at least three-section structure, wherein the first section is of a boss structure and is used for installing a wheel disc rotor to be tested; the second section is of a force measuring pull rod section structure with a smaller diameter and is used for measuring the integral axial dynamic load of the blade; the third section is a boss structure and is used for mounting a specially designed force measuring claw disc which is used for measuring the axial loads of a plurality of blades simultaneously and transmitting the loads to the mandrel; the outer edge of the force measuring claw disc is provided with a plurality of flower claws, and the flower claws are close to the mortise of the gas compressor and are used for bearing the axial force of the blade in the mortise in the high-speed rotation process and preventing the blade from sliding out of the mortise; the strain gauge is attached to the position of the force measuring pull rod section of the mandrel and the position of the flower claw of the force measuring claw disc, the force measuring pull rod section and the flower claw can deform when bearing loads, the strain gauge records the deformation of the corresponding position in real time, converts the deformation into an electric signal and transmits the electric signal to the strain gauge, the strain gauge processes the signal and transmits the data to the computer, and the computer converts the strain into the load and displays the load in real time.
Specifically, the mandrel is of a central through hole structure and is used for connecting a measuring lead in a penetrating manner, one section of the measuring lead is connected with a testing strain gauge, and the other section of the measuring lead is led out of a strain gauge outside the test cavity through a central through hole of a driving main shaft and a high-speed electric slip ring in the speed increasing system;
a real-time online display system is designed, data are collected through multi-sensor combination and are converted into a rotating speed of a wheel disc, a total axial load and a single blade axial load to be displayed in real time, a change curve of the blade axial load along with time and a change curve along with speed in a rotating process are obtained, real-time monitoring and recording of dynamic load in a test process are guaranteed, and important reference data are provided for analysis of follow-up blade axial load.
2) The invention realizes the real-time measurement of the axial dynamic load of a single blade and the axial dynamic loads of a plurality of blades through the force measuring claw disc and the force measuring pull rod section, can compare the statistical characteristics of the axial dynamic load test data of the plurality of blades, can further provide a relation model of the friction coefficient of the mortise and the rotating speed through the curve relation of the axial dynamic load and the rotating speed, is used as the boundary condition of finite element calculation for input, and provides accurate and reliable data for design analysis.
3) The axial dynamic load measuring device for the compressor blade is suitable for wheel disc rotors with various structures and sizes, the specific sizes of a core shaft, a gland, a lock and the like can be adjusted according to a test object and test requirements, the axial dynamic load measuring device can also be used for measuring the axial dynamic load of the blade on rotors such as a turbine disc, a fan and the like, the universality is strong, the measuring working condition is close to the real working state, and the data reliability is high.
Drawings
FIG. 1 is a schematic diagram of the main system of an axial dynamic load measuring device for blades of an engine compressor;
FIG. 2 is a schematic structural diagram of an axial dynamic load measuring device for a compressor blade of an engine;
FIG. 3 is a schematic view of a local structure of a measuring tool and a load transmission path;
FIG. 4 is a schematic diagram of a stress cloud of a mandrel and a strain gage;
FIG. 5 is a schematic view of a three-dimensional structure of a measuring claw disk;
FIG. 6 is a flow chart of a compressor blade axial dynamic load measurement test;
FIG. 7 is a real-time curve of rotation speed-time and a real-time curve of vibration-time in the test process; FIG. 8 is a real-time graph of blade and integrated load-rotation speed during the test;
fig. 9 is a schematic physical structure diagram of the load measurement tool.
In the figure, 1, a cavity cover, 2, a cavity wall, 3, a containing ring, 4, a vacuumizer, 5, an acceleration head, 6, a driving spindle, 7, a high-speed electric slip ring, 8, a tooling mandrel, 9, an upper gland, 10, a wheel disc, 11, a blade, 12, a lower gland, 13, a first locking nut, 14, a force measuring claw disc, 15, a claw strain gauge, 16, a measuring lead, 17, a second locking nut, 18, a pull rod strain gauge, 19, a strain gauge, 20, an acceleration system controller, 21, a computer, 22, a rotation speed sensor, 23, a vibration sensor, 24, a mortise, 25, a claw, 26, a pressing end face, 27, a second thread section, 28, a spigot, 29, a through hole, 30, a first thread section, 31, a second matching face, 32, a pull rod section, 33, a shaft shoulder, 34, a force measuring lead, a first matching face, a force measuring lead, a connecting hole, 36, a threaded hole, 37, a boss, 38 and a through hole.
Detailed Description
The invention is further illustrated by the following figures and examples.
As shown in fig. 1-2, the device for measuring the axial dynamic load of the turbine engine blade mainly comprises a closed test cavity, a rotation acceleration system, a load measuring tool, a data acquisition system and the like.
The sealed test cavity comprises a cavity cover 1, a cavity wall 2, a vacuumizing machine 4 and a containing ring 3, the cavity cover 1 and the cavity wall 2 form the sealed test cavity, the vacuumizing machine 4 is connected to the cavity wall, a certain vacuum degree is guaranteed in the cavity to reduce the rotation resistance of the blade during testing, the rotor is enabled to reach a high-speed rotation state, the containing ring 3 is installed on the inner side of the test cavity, the test cavity is prevented from being damaged when accidental flying-off occurs in the high-speed rotation process of the blade, and the safety of test operators is guaranteed.
The rotary speed increasing system mainly comprises a speed increasing head 5, a driving main shaft 6, a speed increasing system controller 20, a fixing mechanism and the like, wherein the speed increasing head is driven by a motor to enable the driving main shaft 6 to rotate at a high speed; the lower end of the driving main shaft 6 is hung with a to-be-tested compressor blade measuring tool, a through hole with the diameter of 8-10mm is formed in the middle of the tool and used for being connected with a measuring lead 16 in a penetrating mode, the measuring lead 16 rotates at a high speed along with the driving main shaft 6, signal transmission is achieved through the high-speed electric slip ring 7 and a static measuring lead outside a cavity, and the rotating speed increasing system is installed on the testing cavity cover 1 through a fixing mechanism, is internally provided with a rotating speed sensor 22 and a vibration sensor 23 and is used for monitoring vibration of the rotating speed of the driving main shaft 6 in real time.
The load measurement frock includes frock dabber 8, goes up gland 9, rim plate 10, blade 11, gland 12, first lock nut 13, dynamometry claw dish 14 and second lock nut 17, the major function of load measurement frock includes: 1) realizing the switching with a driving main shaft, 2) installing a wheel disc rotor to ensure the stable high-speed rotation of the rotating speed of the blades of the compressor, 3) installing a force measuring claw disc to realize the axial dynamic load measurement of a single blade, 4) realizing the overall axial load measurement of all the blades, 5) pasting a strain gauge and leading out signals, and 6) realizing auxiliary functions such as dynamic balance.
Specifically, as shown in fig. 3, in one embodiment of the present invention, a mandrel with a multi-section structure is designed, and the section I is used for realizing the switching between the load measuring tool and the driving spindle 6; the section II is of a boss structure, so that the wheel disc 10 is installed; the section IV is of a boss structure, and the force measuring claw disc 14 is mounted to measure the axial dynamic load of a single blade; the section III is of a force measuring pull rod section structure with a smaller diameter, so that the integral axial load measurement of all the blades is realized; the V section is an auxiliary section and is jointly used for dynamic balance calibration before testing with the I section, and a central through hole of the tool mandrel is used for signal measurement lead arrangement.
The basic principle of the load measurement tool is as follows: the blade is arranged in a mortise 24 of the wheel disc 10, centrifugal force is generated when the blade rotates at high speed, and dynamic load is generated in the axial direction, a stop pin for bearing the axial dynamic load is removed during testing, the axial dynamic load of the blade is prevented from sliding axially, the axial dynamic load of the blade is transmitted to a spline 25 on the outer edge of a force measuring spline 14, the force measuring spline 14 and a second locking nut 17 are in compression fit at a compression end surface 26, therefore, the load on the spline is transmitted to the second locking nut 17 through the force measuring spline 14, the second locking nut 17 is meshed with a tool mandrel 8 through threads, therefore, the load is continuously transmitted to the tool mandrel, the axial load at a second thread section 27 of the tool mandrel acts on a force measuring pull rod at a section III, the design diameter at the position of the force measuring pull rod section 32 is smaller, the deformation is larger, and the size of the axial load can be accurately tested. The pull rod strain gauges 18 and 15 are respectively adhered to the flower claw 25 of the force measuring claw disc and the force measuring pull rod section 32 of the tooling mandrel, axial loads of a single blade and comprehensive axial loads of a plurality of blades are respectively obtained through testing, and signals are transmitted to a strain gauge outside the test cavity through a force measuring lead.
As shown in fig. 4, in one embodiment of the present invention, the tooling mandrel is a central through hole structure, and the spigot 28, the first thread section 30 and the first matching surface 33 form a second section for mounting the wheel disc 10; the shaft shoulder 33, the second threaded section 27 and the second matching surface 31 form an IV section for installing the force measuring claw disc 14; the force measuring pull rod section 32 and the force measuring lead threading hole 34 form a third section; the measurement lead 16 is located in the central through hole 29.
As shown in fig. 5, the force measuring claw disc adopts a revolving body structure and comprises a step disc with a central through hole and a boss, one end of the boss is coaxially fixed on the bottom end face of the step disc, dynamic balance calibration threaded holes 36 are uniformly distributed at the other end of the boss along the circumferential direction of the central through hole, and a through hole 38 communicated with the central through hole is formed in the side wall of the boss; the outer edge part of the stepped disc is provided with flower claws 25 which correspond to the mortises 24 of the wheel disc 10 one by one, and the flower claws are abutted against the blades and used for bearing the axial force of the blades in the mortises in the high-speed rotation process and preventing the blades from sliding out of the mortises. The outer edge of the disc is provided with a reasonable number of force measuring flower claws 25 according to the number of the blades to be measured, so that the aim of simultaneously measuring a plurality of blades is fulfilled. The flower claw is elastically bent under the action of axial load of the blade, compression elastic strain is formed on one side back to the blade, a flower claw strain gauge 15 is adhered to the middle of the surface, the bending deformation of the flower claw is guaranteed to be linearly distributed in the strain gauge adhering range, then a deformation signal is led out through a through hole 38 by a measuring lead 16, and further led out to an external strain gauge through a central through hole 29 of a tooling mandrel, a through hole of a driving spindle 6 and an electric slip ring 7.
The force measuring jaw disc design boss 37 is used for avoiding the force measuring pull rod section 32 of the mandrel when being assembled with the mandrel 8, increasing the contact length with the mandrel and avoiding the clamping during axial movement.
And a threaded hole 36 is machined on a boss 37 of the force measuring claw disc along the circumferential direction and is used for dynamic balance calibration before a rotor test.
In one specific implementation of the invention, the wheel disc 10 is fixed on the mandrel spigot by an upper gland 9, a lower gland 12 and a first locking nut 13, and the upper cover plate 9 and the lower cover plate 12 jointly act to press the wheel disc 10; the first lock nut 13 abuts against the lower gland 12 and provides a locking force.
In this embodiment, the mandrel 8 is made of titanium alloy, the mandrel drives the upper gland and the lower gland through friction force when rotating, so as to drive the wheel disc to rotate, the blades are installed in the mortises of the wheel disc 10, one side of each blade is fixed by the locking plates and is not stressed, the blades only are used for preventing the blades from falling off when the rotor is carried, and the other side of each blade is fixed by the flower claws 25 on the force measuring claw disc.
The force measuring claw disc 14 is made of high-strength steel and is fixed on a shaft shoulder 31 of the mandrel 8 through a second locking nut 17, and the force measuring claw disc 14 rotates to transmit torque through friction to drive. Particularly, the matching surface 31 of the force measuring claw disc 14 and the second matching surface of the mandrel 8 is a double-matching-surface bridge type mounting structure, the distance between the two ends is not less than 40mm, the force measuring claw disc is used for ensuring the centering of the force measuring claw disc in the high-speed rotation process, and the force measuring pull rod section 32 is arranged between the two ends.
As shown in fig. 3, the assembled blade axial dynamic load measuring tool comprises a mandrel, an upper gland, a lower gland, a lock nut, a wheel disc, a rotor and a force measuring claw disc, wherein the minimum diameter of the mandrel is larger than 10mm so as to ensure the rigidity of the mandrel; the diameter of the upper and lower press covers is D, the thickness of the upper and lower press covers is t, t is more than or equal to D/10, and the pressing force of the measuring tool during assembly is at least greater than the rotor weight multiplied by 100 (newtons), so that sufficient friction force is provided, and the stability of a rotation test is ensured.
In one specific implementation of the invention, a real-time data acquisition system is designed, and the data is acquired through multi-sensor combination, converted into single-blade axial dynamic load, multi-blade axial dynamic load and spindle rotation speed and displayed in real time, so as to obtain a change curve of the axial dynamic load along with time and a change curve along with the rotation speed in the rotation process of the compressor blade, and provide reference data for subsequent blade axial dynamic load data analysis and structure design.
In one specific implementation of the invention, a pull rod strain gauge 18 adhered to a force measuring pull rod section of a tool mandrel is a universal 2% range one-way strain gauge, the force measuring direction is axial, the number of the strain gauges is 4, the strain gauges are uniformly distributed on the force measuring pull rod section for one circle, the interval between adjacent strain gauges is 90 degrees, a universal 2% range flower claw strain gauge 15 is adhered to a flower claw of a force measuring flower disc, the adhering surface is the side of the force measuring flower claw, which is opposite to a blade, the used strain gauge has good fatigue strength, anti-interference performance and self-adaptive compensation functions, the tangential strength of the adhered strain gauge is greater than the centrifugal force borne by the strain gauge, and the strain gauge is prevented from flying out. The measuring lead wire connected with the strain gauge has smaller resistance and flexibility, is convenient to arrange on a measuring tool, is connected to an external static measuring lead wire through holes of a mandrel, a driving main shaft and a high-speed electric slip ring, is finally connected with the strain gauge 19, has a temporary data quick storage function, is powered by 220V voltage, transmits data of the strain gauge to a computer display 21, and displays dynamic loads of blades in real time after being processed by software.
The speed sensor is arranged on a driving main shaft 6 of the rotary speed increasing system and used for detecting the rotating speed of the driving main shaft, a signal line of the speed sensor is connected with a speed increasing system controller 20, the speed increasing system controller can be preset with a speed increasing program, the speed increasing process of the rotor is controlled through actually measured rotating speed signals, the speed increasing system controller transmits data to a computer display 21, and the rotating speed value is displayed in real time after being processed by software. The rotating speed sensor has high rigidity so as to prevent vibration from occurring in the test process and influencing the measurement precision.
The computer software displays the window in real time, the rotating speed is directly read by the rotating speed sensor, the axial dynamic load of a single blade obtained by the force measuring claw disc is calculated and given by the signal data of the claw strain gauge 15 according to the following formula:
Fi＝εi×E 1 ×W/h
wherein Fi is the axial dynamic load of a single blade, epsilon i is the strain data measured by a floral claw strain gauge 15 arranged on the floral claw for measuring force, E 1 The elastic modulus of the material of the force measuring claw disc is W, the bending section coefficient of the flower claw is W, and the distance from the central position of the flower claw strain gauge 15 to the joint of the root of the flower claw and the disc body is h.
The axial comprehensive dynamic load of a plurality of blades obtained by the force measuring pull rod section is calculated by the signal data of the pull rod strain gauge 18 according to the following formula:
Ft＝εj×E 2 ×S
wherein Ft is the axial comprehensive dynamic load of a plurality of blades, epsilon j is the strain data measured by a pull rod strain gauge 18 arranged on the force measuring pull rod section, E 2 The elastic modulus of the material of the mandrel and S is the force measurementCross-sectional area of the tie rod segment.
In one embodiment of the invention, the tie rod load and the claw load may be calibrated prior to testing in order to obtain more accurate dynamic load calculations.
As shown in FIG. 6, the method for measuring the axial dynamic load of the compressor blade of the turbine engine by the device comprises the following steps:
1) Measuring the inner hole diameter and the outer edge diameter of the force measuring pull rod section of the tooling mandrel by using a standard micrometer, uniformly distributing the measurement data circumferentially, taking the average value, and recording the measurement data which is not less than 8;
2) 2-8 strain gauges are adhered to the circumferential direction of a force measuring pull rod section of a tooling mandrel, the measuring range of the strain gauge is 20000 mu epsilon, the tooling mandrel is connected with a strain gauge, the tooling mandrel is installed on a universal testing machine, a tensile load is given, a strain measurement result is detected, the relation between the load and deformation of the force measuring pull rod section is verified by combining the size measurement data of the force measuring pull rod section, a force measuring pull rod section calibration result within the range of 10000 mu epsilon is given, and a paw correction coefficient alpha is obtained;
Fi’＝εi×E 1 ×W/h×α
3) Numbering the flower claws on the force-measuring flower claw disc in sequence, measuring the length and the width of the cross section of each flower claw by using a standard micrometer, taking an average value, and recording at least 8 test data;
4) Pasting a strain gauge on the force-measuring gripper, wherein the range of the strain gauge is 20000 mu epsilon, connecting the strain gauge with the force-measuring gripper, mounting the force-measuring gripper disc on a universal testing machine, applying bending load to the force-measuring gripper, detecting a strain measurement result, verifying the relation between the bending load and deformation of the force-measuring gripper by combining the size measurement data of the gripper, and giving a force-measuring gripper calibration result within the range of 10000 mu epsilon to obtain a gripper correction coefficient beta;
Ft’＝εj×E 2 ×S×β
5) Leading out the strain gage wiring on the tool mandrel and the strain gage wiring on the force measuring claw disc to an external strain gage through a central through hole of the mandrel, carrying out speed increasing and reducing tests according to the highest test rotating speed, recording rotating speed-strain measurement results, and obtaining a zero drift correction coefficient gamma according to the following formula:
ε+γ×ω^2＝0
wherein epsilon is the deformation in the rotation process, and omega is the rotation speed.
6) The wheel disc 10 is installed on a tool mandrel by adopting an upper gland 9, a lower gland 12 and a first lock nut 13, then a blade to be tested is assembled in a mortise on the outer edge of the wheel disc 10, a stop pin in the sliding direction of the blade is removed, and a lock plate is installed in the other direction to prevent the blade from moving in the other direction;
7) A second locking nut is adopted to install the force measuring claw disc on the mandrel, and the positions of the flower claws of the force measuring claw disc are opposite to the blades and used for measuring the axial dynamic load of the blades;
8) Carrying out dynamic balance on the assembled whole measuring rotor to ensure that the dynamic balance precision is not more than 2g.mm, then connecting the measuring rotor to the lower end of a driving main shaft 6, and detecting that the runout degree of the outer edge of the rotor is not more than 0.05mm;
9) An electric slip ring is arranged on the upper part of a test bed driving main shaft, a strain gage wiring on a tooling mandrel and a strain gage wiring on a force measuring claw disc are led out to an external strain gauge through a central through hole of the mandrel and the electric slip ring, the strain gauge is connected to a computer, and the computer receives data for real-time processing, converts the data into a load and displays the load;
10 Considering the product precision problem of power system and sensor group, the set rotating speed overshoot is not more than 20r/min, the strain deformation overshoot is not more than 0.8 percent, namely 8000 mu epsilon, the test result is ensured to be in the calibration result range, and the inaccurate measurement result caused by overhigh rotating speed or overlarge deformation is prevented;
11 Closed test chamber cover), preset test control parameters including target rotational speed value, maximum vibration value, maximum strain value, maximum axial load, acceleration range of rising/falling speed and stable holding time, wherein:
acceleration of rising/falling speed: 3-10r/min/s, the preferred raising speed is 5r/min/s, and the preferred lowering speed is 10r/min/s; stable holding time: 0.5-30min, preferably 3min; maximum vibration value: 150-200 μm; target rotation speed value: determining the maximum working speed of the blade according to test conditions;
12 The measuring device starts to rotate and increase the speed, the rotating speed, the main shaft vibration, the axial load of a single blade and the axial loads of a plurality of blades are displayed in real time through a data acquisition system, a rotating speed-time real-time curve and a vibration-time real-time curve are shown in a figure 7, the maximum working rotating speed of the blade with the axial load to be measured is divided into a plurality of stages (5-8 stages), the rotating speed is firstly stably increased, the rotating speed is kept unchanged for 3min after reaching a certain stage, then the rotating speed is continuously increased until reaching the final rotating speed, and the rotating speed is stably reduced according to an increasing speed program after being kept for 3min, so that the accuracy of a measuring result and the comprehensiveness of the test can be ensured, the vibration reaches the maximum value at a certain stage, the small vibration of other rotating speeds is small, and the maximum value cannot exceed a preset vibration limit value;
the real-time curve of the axial dynamic load and the rotating speed is shown in fig. 8, and the axial dynamic load is continuously increased along with the increase of the rotating speed;
the calculation formula of the axial dynamic load of the single blade is as follows:
Fi＝εi×E 1 ×W/h×α+γ×ω^2
wherein Fi is the axial dynamic load of a single blade, epsilon i is the deformation of the first strain gauge, E 1 The material elasticity modulus of the force measuring claw disc is W, the bending resistance section coefficient of the claw is W, the distance from the central position of the first strain gauge to the joint of the root of the claw and the disc body is h, the claw correction coefficient is alpha, the drift correction coefficient is gamma, and the rotating speed is omega;
the calculation formula of the integral axial dynamic load of all the blades is as follows:
Ft＝εj×E 2 ×S×β
wherein Ft is the axial comprehensive dynamic load of a plurality of blades, epsilon j is the deformation measured by the second strain gauge, E 2 The elastic modulus of the material of the mandrel, S is the section area of the force measuring pull rod section, beta is a pull rod correction coefficient, gamma is a drift correction coefficient, and omega is a rotating speed;
13 Giving a plurality of maximum axial load limit values Ftm of the blades, a single maximum axial load limit value Fim of the blades and a single maximum axial load difference value Fid of the blades, and judging the axial dynamic load state of the blades in the test process in real time according to load-rotating speed data; if the Ftm, the Fim and the Fid do not reach the limit value, continuing the test until the highest rotating speed is reached, and if a certain result reaches the limit value, directly reducing the speed to zero so as to protect the testing machine;
14 ) after the test is finished, deflating after the strain measurement result is confirmed to return to zero, opening the cavity cover, replacing the blades of the compressor, and continuing to carry out related tests;
the axial dynamic load of a single blade is measured by arranging the force measuring claw disc and adhering the strain gauge, so that the simultaneous online measurement of the axial dynamic loads of a plurality of blades of the gas compressor in a high-speed rotating state is realized, the measurement efficiency is increased, the measurement is close to the real working condition, meanwhile, the force measuring pull rod section is designed on the tool mandrel, and the strain gauge is adhered on the force measuring pull rod section, so that the axial load jointly generated by the plurality of blades can be measured, the comparison and analysis are convenient, and more reliable experimental data are provided for the analysis and design. The online real-time measurement, calculation and judgment of data are realized by combining the high-speed slip ring, the strain gauge and the data analysis system. Therefore, the device and the method meet the dynamic load measurement requirement of the compressor blade in a vacuum high-speed rotating state, have the advantages of high measurement efficiency, high test precision, wide structural adaptability, approximate real working condition and the like, solve the problem that the axial dynamic load of the conventional blade high-speed rotating turntable cannot be measured, provide more comprehensive test data support for the optimized design of the blade, the compressor and other structures, and simultaneously can be used for the load measurement of other tenon joint structures, such as turbine blades and the like.
The foregoing lists merely illustrate specific embodiments of the invention. It is obvious that the invention is not limited to the above embodiments, but that many variations are possible. All modifications which can be derived or suggested by the person skilled in the art from the present disclosure are to be considered within the scope of the present invention.
Claims (10)
1. A blade axial dynamic load measuring device is characterized by comprising a closed test cavity, a rotating speed-increasing system, a load measuring tool and a data acquisition system; the rotating speed-increasing system is arranged on a cavity cover of the closed test cavity; the load measuring tool is positioned in the closed test cavity and is connected with the rotating speed increasing system; the data acquisition system is used for acquiring test data in real time during testing;
the load measuring tool comprises a tool mandrel (8), a wheel disc (10), blades (11), a force measuring claw disc (14) and a pressing device, wherein the top of the tool mandrel (8) is connected with a power output end of a rotating speed increasing system, the wheel disc (10) and the force measuring claw disc (14) are fixed on the tool mandrel (8) through the pressing device, the wheel disc (10) is located on the force measuring claw disc (14), and the blades are installed in a mortise (24) of the wheel disc (10);
and strain gauges are arranged on the force measuring claw disc (14) and the tooling mandrel (8) and are respectively used for measuring the axial dynamic load of a single blade and the integral axial dynamic load of all blades.
2. The device for measuring the axial dynamic load of the blade as claimed in claim 1, wherein the force measuring claw disc (14) is of a revolving body structure and comprises a stepped disc with a central through hole and a boss, one end of the boss is coaxially fixed on the bottom end face of the stepped disc, dynamic balance calibration threaded holes (35) are uniformly distributed at the other end of the boss along the circumferential direction of the central through hole, and the side wall of the boss is provided with a through hole (38) communicated with the central through hole; the outer edge of the stepped disc is provided with flower claws (25) which correspond to the mortises (24) of the wheel disc (10) one by one, and the flower claws are abutted against the side faces of the blade tenons.
3. The device for measuring the axial dynamic load of the blade as claimed in claim 2, characterized in that a first strain gauge for measuring the axial dynamic load of the single blade is arranged on one side of the flower claw (25) facing away from the mortise (24).
4. The device for measuring the axial dynamic load of the blade according to claim 3, wherein the tool mandrel (8) comprises a connecting section, a first boss section, a second boss section and an auxiliary section which are sequentially connected; the connecting section is used for connecting a power output end of the rotary speed increasing system, the first boss section is used for positioning the wheel disc (10), and the second boss section is used for positioning the force measuring claw disc (14); and a force measuring pull rod section with a smaller diameter is also arranged on the second boss section.
5. The device for measuring the axial dynamic load of the blade as claimed in claim 4, wherein the first boss section and the second boss section are provided with local thread sections, a second matching surface (31) for mounting the force measuring claw disc (14) is arranged behind the local thread section of the first boss section and in front of the local thread section of the second boss section, the second matching surface (31) is matched with the inner wall of the central through hole of the force measuring claw disc (14), and the force measuring pull rod section is positioned in the central through hole of the force measuring claw disc (14); a first matching surface (35) used for installing the wheel disc (10) is arranged in front of the local thread section of the first boss section, and the first matching surface (35) is matched with the inner wall of the central through hole of the wheel disc (10).
6. The device as claimed in claim 4, wherein the outer wall of the dynamometric tie rod segment is provided with second strain gauges for measuring the overall axial dynamic load of all the blades, and the second strain gauges are uniformly distributed along the circumferential direction.
7. The device for measuring the axial dynamic load of the blade as claimed in claim 4, wherein the pressing device comprises an upper pressing cover (9), a lower pressing cover (12), a first locking nut (13) and a second locking nut (17); the upper gland (9) is sleeved at a boss of the first boss section of the tooling mandrel (8) and used for fixing the top of the wheel disc (10); the lower gland (12) is sleeved at the tail part of the first boss section of the tooling mandrel (8) and is matched with the local thread section on the first boss section through a first locking nut (13) for fixing the bottom of the wheel disc (10);
and the second locking nut (17) is matched with the partial thread section on the second boss section and is used for fixing the bottom of the force measuring claw disc (14).
8. The device for measuring the axial dynamic load of the blade as claimed in claim 1, wherein the data acquisition system comprises a strain gauge, a rotating speed sensor, a vibration sensor and a high-speed electric slip ring measurement lead; the high-speed electric slip ring measuring lead is used for connecting a strain gauge and a strain gauge, the rotating speed sensor and the vibration sensor are installed on the rotating speed-increasing system, and the output ends of the strain gauge, the vibration sensor and the rotating speed sensor are connected with an external computer.
9. A measuring method based on the blade axial dynamic load measuring device of claim 6, characterized by comprising the following steps:
1) A preparation stage:
1.1 Calibrating the relation between bending load and strain borne by the gripper of the gripper disc (14) to obtain the calibration result of the gripper disc (14) in the working range, and fitting the calibration result according to the following formula to obtain a gripper correction coefficient alpha;
Fi’＝εi×E 1 ×W/h×α
wherein Fi' is the flower claw calibration load, epsilon i is the flower claw calibration strain, E 1 The material elasticity modulus of the force measuring claw disc is W, the bending resistance section coefficient of the claw is W, and h is the distance from the center of the first strain gauge to the joint of the root of the claw and the disc body;
1.2 Calibrating the relation between the load and the strain of a force-measuring pull rod section in a testing tool mandrel to obtain a calibration result of the force-measuring pull rod section in a working range, and fitting the calibration result according to the following formula to obtain a pull rod correction coefficient beta;
Ft’＝εj×E 2 ×S×β
wherein Ft' is the pull rod calibration load, epsilon j is the pull rod calibration strain, E 2 The elastic modulus of the material of the mandrel is S, and the section area of the force measuring pull rod section is S;
1.3 A tool mandrel is arranged at the power output end of the rotary speed-increasing system, and a wheel disc (10) and a force measuring claw disc (14) are fixed on the tool mandrel;
1.4 Lead out the strain gauge wiring on the tooling mandrel and the strain gauge wiring on the force measuring claw disc to an external strain gauge through a central through hole of the mandrel, perform speed-up and speed-down tests according to the highest test rotating speed, record the rotating speed-strain measurement result, and obtain a zero drift correction coefficient gamma according to the following formula:
ε+γ×ω^2＝0
wherein epsilon is the average strain of the first strain gauge on the flower claw and the second strain gauge on the pull rod in the rotation process, and omega is the rotation speed;
2) And (3) a testing stage:
2.1 Vacuumizing the sealed test cavity, setting a target rotating speed value, a speed rising/reducing acceleration range and stable holding time, and setting a maximum vibration value, a maximum strain value and a maximum axial load;
2.2 The blade is arranged on the measuring device, the starting device and the rotating speed-increasing system drive the load measuring tool to rotate and increase the speed, the blade generates centrifugal force and generates dynamic load in the axial direction when rotating at high speed, the axial dynamic load of the blade is transmitted to the flower claw (25) on the outer edge of the force measuring claw disc (14), and the strain is measured by the first strain gauge; the dynamic load on the flower claw (25) is transmitted to a second matching surface (31) of the tool mandrel through the force measuring claw disc (14) and then acts on the force measuring pull rod section, and the axial load can be accurately tested due to the fact that the force measuring pull rod section is small in diameter and large in deformation, and the strain is measured through the second strain gauge;
real-time displaying the rotating speed, the main shaft vibration, the axial dynamic load of a single blade and the integral axial dynamic load of all blades through a data acquisition system to obtain a rotating speed-time real-time curve, a vibration-time real-time curve and an axial dynamic load-rotating speed real-time curve;
the calculation formula of the axial dynamic load of the single blade is as follows:
Fi＝εi×E 1 ×W/h×α+γ×ω^2
fi is the axial dynamic load of a single blade;
the calculation formula of the integral axial dynamic load of all the blades is as follows:
Ft＝εj×E 2 ×S×β
wherein Ft is the axial comprehensive dynamic load of a plurality of blades;
3) And after the test is finished, filling air into the test cavity after the rotating speed is reset to zero.
10. A measuring method of the blade axial dynamic load measuring device of claim 9 is characterized in that in a testing stage, a plurality of blade maximum axial load limiting values Ftm, a single blade maximum axial load limiting value Fim and a single blade axial load maximum difference value Fid are given, an axial dynamic load-rotating speed real-time curve is given, and the state of the blade axial dynamic load in the testing process is judged; if the Ftm, the Fim and the Fid do not reach the limit value, continuing the test until the highest test rotating speed is reached, and if any one of the Ftm, the Fim and the Fid reaches the limit value, directly reducing the speed to zero so as to protect the device.
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