Ultrahigh-frequency friction-wear test device based on excitation response

Abstract

The invention provides an ultrahigh-frequency friction-wear test device based on excitation response, and relates to the field of friction-wear tests, the ultrahigh-frequency friction-wear test device comprises a computer system, a test data acquisition and control system and a high-frequency vibration driving system which are connected in sequence, and the vibration driving system is provided with a sensor and a test device; the computer system is used for setting vibration parameters, executing test control commands, monitoring real-time signals and analyzing later data; the test data acquisition and control system is used for receiving multi-channel acceleration and displacement signals from the sensor and outputting driving signals to the high-frequency vibration driving system; and the high-frequency vibration driving system is used for generating an excitation load with specific frequency and amplitude, and applying dynamic energy to the test device, so that the test device generates controlled vibration response in a structural mode. According to the invention, the frictional contact behavior of the wear-resistant material in the actual working condition can be simulated through high-frequency vibration under the resonance state of the whole structure, and the system evaluation of the frictional wear performance of the wear-resistant material is realized.

Description

Technical Field

[0001] This invention relates to the field of friction and wear testing technology, and specifically to an ultra-high frequency friction and wear testing device based on excitation response. Background Technology

[0002] In the field of materials service performance research, wear-resistant materials, as crucial friction pairs in key components of mechanical equipment and aero-engines, directly affect the service life and reliability of these devices. In existing friction and wear tests of wear-resistant materials, traditional devices typically employ a single loading method, such as reciprocating linear or rotational loading characteristics. This method is simplistic and inefficient, failing to comprehensively simulate actual working conditions. Secondly, existing friction and wear testing devices mostly employ static or low-frequency loading, making it difficult to accurately acquire dynamic contact forces under high-frequency vibration conditions in real time, thus hindering the accurate evaluation of the frictional performance of wear-resistant materials under real-world conditions. Furthermore, the fixed contact angle of existing test samples lacks the ability to quantitatively assess the friction-wear of the tested samples, limiting research on the systematic evaluation of material friction and wear performance under different working conditions. Additionally, the limited data processing channels of traditional friction and wear testing devices make it difficult to achieve simultaneous acquisition and analysis of multiple sensors, limiting a comprehensive understanding of friction-wear behavior. Therefore, existing technologies are insufficient to meet the comprehensive requirements of high-frequency vibration, dynamic loading, adjustable angles, and simultaneous acquisition of multi-channel data. A novel friction and wear testing device for wear-resistant materials is urgently needed to overcome these technical bottlenecks. Summary of the Invention

[0003] In view of this, this application provides an ultra-high frequency friction and wear testing device based on excitation response. This device can simulate the frictional contact behavior of wear-resistant materials under actual working conditions through high-frequency vibration under the overall structural resonance state. It also features contact angle adjustment and dynamic mechanical measurement functions, enabling a systematic evaluation of the friction and wear performance of wear-resistant materials. Its applications cover the performance evaluation and optimization of wear-resistant materials, friction materials, and related components, providing a scientific and technical means for high-precision, repeatable friction and wear performance experiments. Furthermore, it can support the design, material selection, and life prediction of wear-resistant components in fields such as aerospace, energy, and machinery manufacturing.

[0004] This application provides the following technical solution: an ultra-high frequency friction and wear testing device based on excitation response, comprising: a computer system, a test data acquisition and control system, and a high frequency vibration drive system connected in sequence, wherein a sensor system and a testing device are provided on the high frequency vibration drive system;

[0005] The computer system serves as the core control and information processing unit of the entire test system, used to set vibration parameters, execute test control commands, monitor real-time signals, and perform subsequent data analysis. The test data acquisition and control system is used to receive multi-channel acceleration and displacement signals from the sensor system, complete data acquisition and signal conversion; and output drive signals to the high-frequency vibration drive system according to the control commands issued by the computer system and the set control algorithm, so as to realize closed-loop control of test loading. The high-frequency vibration drive system is used to generate an excitation load of a specific frequency and amplitude according to the control signal issued by the test data acquisition and control system, and to apply dynamic energy to the test device so that the test device generates a controlled vibration response under structural modes. The main load-bearing structure of the test device is a cylindrical loading frame, which includes a lower flange base, a middle main load-bearing structure, and an upper connecting and positioning part. The middle main load-bearing structure adopts a hollowed-out cylindrical support rib structure, which is fixed to the lower flange base. The upper connecting and positioning part includes a cover plate, which is fixed to the top opening of the support rib structure. The test device also includes a first connector, a second connector, an upper sample, and a lower sample. A first connecting groove is formed in the center of the inner wall of the cover plate, and a second connecting groove is formed in the center of the lower flange base. The upper sample is fixed to the first connector, which is fixedly installed in the first connecting groove. The lower sample is fixed to the second connector, which is fixedly installed in the second connecting groove, so that the upper sample and the lower sample are in contact with each other to form a friction pair. The upper and lower specimens have the same structure, both adopting a wedge-shaped oblique truncated quadrangular prism structure, so that the oblique section of the oblique truncated quadrangular prism structure forms an adjustable angle θ with the bottom surface, and the oblique sections of the upper and lower specimens are in contact with each other as the test surfaces.

[0006] According to one embodiment of this application, the sensor system includes an acceleration sensor, a displacement sensor, and a force sensor. An acceleration sensor is disposed on the top of the high-frequency vibration drive system, and an acceleration sensor and a displacement sensor are disposed on the top of the test device. The force sensor is arranged in the second connecting groove.

[0007] According to one embodiment of this application, the lower flange base is in the shape of a flat disc and is fixed to the high-frequency vibration drive system by bolts, providing a stable installation reference and constraint for the test device in a resonant state.

[0008] According to one embodiment of this application, the cover plate is a disc structure, with bolt holes and positioning holes arranged on the outer edge for fixing to the top opening of the supporting rib structure, and a boss and the first connecting groove provided on the plate surface for fixing to the first connecting head and the upper sample to achieve geometric positioning and mechanical load transfer.

[0009] According to one embodiment of this application, the test apparatus further includes a gasket located between the cover plate and the top opening of the support rib structure.

[0010] According to one embodiment of this application, the gasket includes a first gasket, a second gasket, and a third gasket. The first and second gaskets are generally in annular shape and are provided with positioning holes and U-shaped grooves. The third gasket is provided with positioning holes, U-shaped grooves, and bosses.

[0011] According to one embodiment of this application, the upper sample is fastened to the first connector, and the lower sample is fastened to the second connector by bolts.

[0012] According to one embodiment of this application, the support rib structure adopts a thin-walled modal design with a wall thickness of 5mm to 10mm, so that the support rib structure exhibits a modal characteristic of bending around the four sides at a specific frequency.

[0013] The experimental apparatus designed in this invention achieves overall structural resonance through ultra-high frequency vibration drive, simulating the contact behavior of wear-resistant materials under service conditions, thereby obtaining the tribological properties of materials under near-service conditions. By adjusting the contact angle of the test sample, it meets the tribological research needs of materials under different operating conditions. The dynamic force measurement system, combined with inertial compensation, achieves high-precision real-time measurement of normal force, frictional force, and shear force. The modular structural design facilitates sample replacement and apparatus maintenance. This apparatus can systematically and comprehensively evaluate tribological properties under ultra-high frequency conditions, providing a reliable experimental device and method for the research, development, and performance optimization of wear-resistant materials.

[0014] Compared with the prior art, the beneficial effects that the at least one technical solution adopted in the embodiments of the present invention can achieve specifically include the following points: (1) High-frequency vibration drive and structural modal resonance coupling By exciting the modal resonance of the test device's own structure through high-frequency vibration, the wear-resistant material is made to generate frictional contact under vibration conditions close to actual service conditions, thereby achieving a high degree of coupling between friction and wear behavior and structural response, significantly improving the authenticity of the experiment and the reliability of the data.

[0015] (2) Adjustable contact angle and adaptability to multiple working conditions This experimental setup allows for adjustment of the contact surface angle of wear-resistant materials using adjustable tilt specimens, covering a range of operating conditions and simulating friction and wear behavior under actual service conditions. Combined with high-frequency vibration loading, this design enables systematic research into friction mechanisms and damage evolution under different contact states, improving the representativeness and reliability of experimental data. It also overcomes the limitations of traditional fixed-angle setups, enhancing the adaptability and versatility of the device.

[0016] (3) High-precision dynamic force measurement and multi-channel synchronous acquisition By combining a dynamic force measurement system with inertial compensation technology, real-time high-precision measurement of normal force, friction force, and shear force of wear-resistant materials under high-frequency vibration is achieved. At the same time, multi-channel synchronous acquisition and processing ensure the consistency of force, displacement, acceleration, and other signals, providing comprehensive and scientific data support for friction and wear performance.

[0017] (4) Modular structural design and systematic friction and wear assessment This device adopts a modular design, and the core testing area, vibration drive system and force measurement system can be disassembled and maintained independently, which facilitates sample replacement. The whole device can systematically and comprehensively evaluate the friction and wear characteristics of wear-resistant materials under high-frequency vibration and adjustable contact angle conditions, realize high-precision and repeatable tribological experiments, and provide a reliable experimental platform for material design and evaluation. Attached Figure Description

[0018] To more clearly illustrate the technical solutions of the embodiments of this application, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0019] Figure 1 This is an overall schematic diagram of the ultra-high frequency friction and wear testing device based on excitation response according to an embodiment of the present invention; Figure 2 This is a schematic diagram of the modal distribution characteristics in the initial state of an embodiment of the present invention; Figure 3 This is a schematic diagram showing the state of significant deformation of the device under specific frequency excitation according to an embodiment of the present invention; Figure 4 This is a flowchart illustrating the overall system design concept of an embodiment of the present invention; Figure 5 This is a first structural schematic diagram of the experimental apparatus according to an embodiment of the present invention; Figure 6 This is a second structural schematic diagram of the test apparatus according to an embodiment of the present invention; Figure 7 This is a third structural schematic diagram of the experimental apparatus according to an embodiment of the present invention; Figure 8 This is a fourth structural schematic diagram of the experimental apparatus according to an embodiment of the present invention; Figure 9 This is a first structural schematic diagram of the gasket according to an embodiment of the present invention; Figure 10 This is a schematic diagram of the second structure of the gasket in an embodiment of the present invention; Figure 11This is a first structural schematic diagram of the sample in an embodiment of the present invention; Figure 12 This is a second structural schematic diagram of the sample in an embodiment of the present invention; Figure 13 This is a schematic diagram of the connector structure according to an embodiment of the present invention; Figure 14 This is a schematic diagram of force decomposition in an embodiment of the present invention; Among them, 1-computer system, 2-experimental data acquisition and control system, 3-high frequency vibration drive system, 401-accelerometer, 402-displacement sensor, 403-force sensor, 5-experimental device, 551-bolt hole, 552-support rib, 553-hollowed-out, 554-fixing bolt hole, 555-flange base, 556-groove, 557-assembly positioning hole, 558-connecting groove, 510-cover plate, 520-gasket, 530-connector, 540-sample, 550-main load-bearing structure, 521-bore, 522-first layer gasket, 523-second layer gasket, 524-third layer gasket, 525-gasket positioning hole, 526-U-groove, 541-sample assessment surface, 542-sample bottom. Detailed Implementation

[0020] The embodiments of this application will now be described in detail with reference to the accompanying drawings.

[0021] The following specific examples illustrate the implementation of this application. Those skilled in the art can easily understand other advantages and effects of this application from the content disclosed in this specification. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of them. This application can also be implemented or applied through other different specific embodiments, and the details in this specification can also be modified or changed based on different viewpoints and applications without departing from the spirit of this application. It should be noted that, in the absence of conflict, the following embodiments and features in the embodiments can be combined with each other. Based on the embodiments in this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0022] like Figures 1-14 As shown, this invention provides a system for comprehensively evaluating the tribological characteristics of wear-resistant materials under high-frequency vibration and adjustable contact angle conditions, achieving high-precision and repeatable tribological experiments, and providing a reliable experimental platform for the design, performance optimization, and life prediction of wear-resistant materials. The ultra-high frequency tribological testing device based on excitation response of this invention includes: a computer system 1, a test data acquisition and control system 2, and a high-frequency vibration drive system 3 connected in sequence. The high-frequency vibration drive system 3 is equipped with a sensor system and a testing device 5. The computer system 1 serves as the core control and information processing unit of the entire test system, used to set vibration parameters, execute test control commands, monitor real-time signals, and perform subsequent data analysis. The test data acquisition and control system 2 is used to receive multi-channel acceleration and displacement signals from the sensor system, complete data acquisition and signal conversion; and according to the control commands issued by the computer system 1, output drive signals to the high-frequency vibration drive system 3 according to the set control algorithm to realize closed-loop control of test loading. The high-frequency vibration drive system 3 is used to generate an excitation load of a specific frequency and amplitude according to the control signal issued by the test data acquisition and control system 2, and to apply dynamic energy to the test device 5, so that the test device 5 generates a controlled vibration response under structural modes. The main load-bearing structure 550 of the test device 5 is a cylindrical loading frame. The loading frame includes a lower flange base, a middle main load-bearing structure, and an upper connecting and positioning part. The middle main load-bearing structure adopts a cylindrical support rib 552 structure with a hollow 553. The support rib 552 structure is fixed on the lower flange base. The upper connecting and positioning part includes a cover plate 510, which is fixed on the top opening of the support rib 552 structure. The test device 5 also includes a first connector, a second connector, an upper sample, and a lower sample. A first connecting groove is opened in the center of the inner wall of the cover plate 510, and a second connecting groove is opened in the center of the lower flange base. The upper sample is fixed to the first connector, which is fixedly installed in the first connecting groove. The lower sample is fixed to the second connector, which is fixedly installed in the second connecting groove, so that the upper sample and the lower sample are in contact with each other to form a friction pair. The upper and lower specimens have the same structure, both adopting a wedge-shaped oblique truncated quadrangular prism structure, so that the oblique section of the oblique truncated quadrangular prism structure forms an adjustable angle θ with the bottom surface, and the oblique sections of the upper and lower specimens are in contact with each other as the test surfaces.

[0023] This invention provides a test device with ultra-high frequency vibration drive, adjustable friction contact angle, and accurate dynamic force measurement. Its main load-bearing structure is a circular loading frame with high overall rigidity and excellent vibration resistance, consisting of a lower flange base, a middle main load-bearing structure, and an upper connecting and positioning part. The device uses a high-frequency vibration drive system to excite resonance in the overall structure, thereby simulating the friction contact behavior of the sample during near-service vibration. The sample can be designed as a wedge-shaped or inclined testing surface. By fixing the connector to the frame and cover plate, reliable loading of the friction pair at different angles is achieved. The dynamic force measurement system, combined with an inertial compensation mechanism, can measure the normal force, friction force, and shear force between wear-resistant materials in real time. Furthermore, the multi-channel data acquisition system ensures simultaneous acquisition and processing of multiple physical quantities such as force, displacement, and acceleration. In addition, the modular structural design facilitates sample replacement and device maintenance, improving the applicability and reliability of the equipment.

[0024] In some embodiments, the structure of this device, from top to bottom, includes a cover plate 510, a gasket 520, a connector 530, a sample 540, and a main bearing structure 550. The main bearing structure 550 is an integral circular loading frame, which can achieve overall structural resonance under high-frequency vibration conditions. The device is equipped with a dynamic force measurement system to acquire the frictional force between the test samples in real time, and combines it with a multi-channel data acquisition and processing system to realize synchronous signal acquisition, analysis, and storage, so as to realize the evaluation of the friction and wear performance of wear-resistant materials under resonance conditions. The resonance response characteristics of the device are achieved through the overall structural design and optimization of parameters such as the distribution, thickness, and hollow ratio of the support ribs.

[0025] In some embodiments, the main bearing structure 550 includes a lower flange base 555, a middle main bearing area, and an upper connection positioning area; the lower flange base 555 is in the shape of a flat disc and is provided with fixing bolt holes 554, which are fixed to an external high-frequency vibration loading device by high-strength bolts, providing a stable installation reference and constraint for the device in the resonance state; the upper connection positioning area is provided with bolt holes 551, assembly positioning holes 557, and grooves 556, which are used for precise assembly with the cover plate 510 and the connector 530 to ensure the geometric accuracy and mechanical continuity of the device under modal resonance conditions.

[0026] The central main bearing area adopts a support rib 552 structure and a large-area hollow 553 design to reduce structural inertia and improve vibration response sensitivity. Through modal optimization design, the upper surface generates axial reciprocating motion at the target frequency, realizing stable dynamic friction loading of wear-resistant materials under structural modal resonance. The resonant frequency of the device can be finely controlled by adjusting the thickness, distribution and hollow ratio of the support ribs, as well as the number of shims.

[0027] The experimental device 5 was designed using finite element analysis and modal simulation to ensure that it exhibits the expected modal response under high-frequency excitation conditions, achieving stable motion of the upper surface of the friction pair at the target frequency. The main load-bearing structure 550 and support ribs 552 of the device are arranged through modal optimization design to ensure that the upper surface generates axial reciprocating motion at the target excitation frequency, achieving stable dynamic friction loading of the wear-resistant material under high-frequency resonance conditions.

[0028] In some embodiments, the cover plate 510 is an integral disc structure with bolt holes and positioning holes arranged on the outer edge, and a boss and connecting groove provided on the plate surface for fixed connection with the connector 530 and the sample 540 to achieve high-precision geometric positioning and mechanical load transfer; an acceleration sensor 401 and a displacement sensor 402 are provided on the top of the cover plate 510 to obtain the dynamic response of the device at the sample contact surface under resonance conditions.

[0029] In some embodiments, the gasket 520 is located between the cover plate 510 and the main frame, and has an annular structure with a boss 521, a gasket positioning hole 525, and a U-shaped groove 526, to achieve precise alignment, mechanical transition, and local stress buffering during assembly. The device adjusts the number of gaskets 520 to change the overall stiffness of the main load-bearing structure 550, thereby achieving adjustable control of the resonant frequency to adapt to the friction and wear test requirements of different wear-resistant materials.

[0030] In some embodiments, the sample 540 is a prism structure with an inclined sample assessment surface 541. The assessment surface and the bottom surface of the sample bottom 542 form an adjustable angle θ to simulate the friction-wear behavior of wear-resistant materials under different contact conditions and to achieve accurate tribological measurement in a high-frequency resonance state.

[0031] In some embodiments, the connector 530 is fastened to the sample by bolts and embedded in the connecting groove 558 of the cover plate 510 and the main frame to ensure that the sample position is stable and the force is continuous under modal resonance conditions, thereby ensuring the high precision and repeatability of the friction and wear test.

[0032] The dynamic force measurement system in the sensor system, combined with an inertial compensation mechanism, can measure the normal force, frictional force, and shear force of wear-resistant materials in real time under high-frequency vibration conditions, and eliminate the influence of the structure's own inertial force and modal deformation on the measurement results. The multi-channel data acquisition and processing system can simultaneously acquire multiple physical quantity signals such as force, displacement, and acceleration, and achieve synchronous processing to ensure the temporal consistency of data and the reliability of experimental results. Under high-frequency vibration conditions, the device forms a closed-loop control system from signal generation, energy loading, friction pair contact, mechanical response measurement to data acquisition and analysis, realizing high-precision and repeatable evaluation of the friction and wear performance of wear-resistant materials.

[0033] In practical implementation, the logical structure of the test control system of this invention mainly consists of a computer system 1, a test data acquisition and control system 2, a high-frequency vibration drive system 3, a sensor system, and a test device 5. The modules form a closed-loop control circuit through signal and energy transmission to achieve dynamic loading and response measurement of the test device at a specific frequency. Figure 1 As shown.

[0034] Computer system 1 serves as the core control and information processing unit of the entire test system, used to set vibration parameters, execute test control commands, monitor real-time signals, and perform subsequent data analysis. The test data acquisition and control system is the signal hub of the system. On the one hand, it receives multi-channel acceleration and displacement signals from the sensor system, completing data acquisition and signal conversion; on the other hand, it outputs drive signals to the high-frequency vibration drive system according to the set control algorithm, realizing closed-loop control of the test loading.

[0035] The high-frequency vibration drive system 3, acting as an energy execution unit, generates an excitation load of specific frequency and amplitude according to the control signal, applying dynamic energy to the test device to induce a controlled vibration response under structural modes. The sensor system includes accelerometers and displacement sensors installed at key locations on the test device, which are used to monitor the dynamic acceleration and displacement changes of the device during vibration, thereby achieving accurate measurement of the system response characteristics.

[0036] The test apparatus 5 is the object under test for the entire system. Its main load-bearing structure is an integral loading frame, which forms a complete friction pair system with the tilt-adjustable sample assembly through the cover plate 510, gasket 520, and connector 530. When the system is excited at a specific frequency, the thin-walled structure of the frame is in a bending mode, and the cover plate moves axially up and down, thereby driving the connector to slide relative to the sample, realizing the friction-wear characteristics test under different tilt angle conditions.

[0037] The sensor system includes two accelerometers 401, a displacement sensor 402, and a force sensor 403. The accelerometers 401 are positioned above the high-frequency vibration drive system 3 to obtain the vibration amplitude of the vibration table. The accelerometers 401 and displacement sensor 402 are positioned above the test device to obtain the force exerted on the test sample under resonance conditions and the axial displacement of the test sample during friction and wear. The force sensor 403 is located in a connecting groove within the test device; its main purpose, as will be described later, is to verify the frictional force of the test sample during the test.

[0038] Through the coordinated operation of the above-described logical structure, this invention achieves a closed-loop control across the entire chain, from signal generation to energy loading, dynamic response, data acquisition, and result analysis. This system boasts advantages such as high response accuracy, strong control stability, and good data traceability, providing reliable experimental support and a technical platform for the study of the friction and wear mechanism of wear-resistant materials under vibration modes.

[0039] The modal response analysis results of the device are as follows: Figure 2 and Figure 3 As shown. Figure 2 The modal distribution characteristics in the initial state are shown. Figure 3 This demonstrates the significant deformation of the device under specific frequency excitation. A comparison reveals that at the resonant frequency, the support rib structure exhibits significant bending deformation, which is directly transmitted to the cover plate and sample assembly, causing periodic displacement along the vertical direction. This phenomenon indicates that when the test device is subjected to vibration excitation matching its natural frequency, it will trigger a reciprocating motion mode centered on the support rib-cover plate linkage system.

[0040] The overall system design concept is as follows: Figure 4 As shown, the experiment mainly consists of two parts: device design and device testing. First, modal analysis of the experimental device is performed using finite element analysis software to obtain its modal response characteristics at different excitation frequencies. This ensures that the device can achieve stable and controllable resonance modes within a specific frequency range, thus meeting the dynamic response requirements of high-frequency friction and wear testing. Based on this, according to the designed experimental device structure and combined with the output characteristics of the high-frequency excitation system, the structural resonance effect is used to achieve high-frequency loading of the material friction pair, thereby systematically evaluating the friction and wear behavior of wear-resistant materials under ultra-high frequency conditions.

[0041] This experimental setup employs a closed-loop control logic encompassing a computer, control system, high-frequency vibration drive system, experimental device, and sensors. It integrates high-frequency excitation, dynamic response measurement, and data analysis functions to achieve real-time monitoring and adaptive control of the experimental process. This design, through the coupling of modal vibration and friction pairs, not only improves the sensitivity and response accuracy of friction and wear tests but also allows for the study of friction mechanisms and damage evolution under different sample angle conditions, providing a novel experimental setup and method for the research of high-performance wear-resistant materials.

[0042] The design principle of the high-frequency vibration-driven friction and wear testing device of this invention is based on the coupling mechanism of structural modal resonance excitation and friction pair dynamic response. By loading the friction pair under controlled resonance, the friction and wear behavior of materials under near-service conditions is simulated under high-frequency vibration conditions, thereby overcoming the limitations of traditional low-frequency or static loading tests in dynamic contact characterization.

[0043] The core principle is that when the driving frequency of the high-frequency vibration equipment approaches the natural frequency of the test device structure, the system enters a resonant state. The sample generates stable and controllable relative motion under high-frequency vibration, so that the frictional stress at the contact interface reaches a level comparable to that of the actual service environment. By precisely controlling the excitation frequency and amplitude, the contact state, stress distribution, and energy input of the friction pair can be adjusted, thereby allowing the study of the friction and wear mechanism of materials under different dynamic loads.

[0044] The system of this invention is designed based on the principle of closed-loop control. The computer system adjusts the excitation signal in real time and collects normal force, friction force, and shear force signals through sensors. The collected signals are filtered and inertial compensation processed in the control and data processing unit of the computer system. By calculating and subtracting the inertial force components introduced by the movement of the loading mechanism, fixtures, and sensors under vibration or resonance conditions based on the system dynamics, an effective force signal reflecting the true stress state of the sample is obtained and fed back to the control system to achieve dynamic steady-state control of the test process. This closed-loop feedback mechanism effectively ensures the operational stability and measurement accuracy under resonance conditions and significantly improves the repeatability and data reliability of experimental results. In addition, the system ensures that the test device has an ideal vibration mode distribution in a specific frequency band through modal analysis and structural dynamics matching design, reducing structural coupling interference and energy dissipation, thereby achieving efficient energy transfer and local response amplification. The adjustable angle structure design of the test module allows the friction behavior under different contact postures to be reproduced, further expanding the applicability of the system in multi-condition friction and wear research.

[0045] In summary, the design principle of this device achieves the organic integration of resonant modal excitation, mechanical response measurement, and intelligent control, providing a high-precision and high-sensitivity experimental method for studying the friction and wear behavior of wear-resistant materials under complex dynamic load environments.

[0046] Innovation: The innovation of this invention lies in introducing the structural modal resonance principle into the friction and wear test of wear-resistant materials. Stable resonant response of the friction pair under specific modes is achieved through high-frequency vibration drive, significantly improving energy transfer efficiency and test sensitivity. Through the dynamic coupling design of the friction pair and structural modes, dynamic control of friction behavior under different angles and frequencies can be realized. The constructed computer-control system-drive device-sensor closed-loop adaptive control system can correct the excitation signal in real time and maintain steady-state excitation. Simultaneously, the synchronous acquisition and data fusion of multi-channel acceleration, displacement, and force signals provide multi-dimensional information support for the dynamic characteristic analysis of the friction interface. This design overcomes the limitations of traditional friction and wear devices, such as low excitation frequency, poor control accuracy, and limited test dimensions, providing a new experimental platform and technical path for the study of the friction and wear mechanism of wear-resistant materials under high-frequency vibration conditions.

[0047] Feasibility: This invention, through an integral circular loading frame and thin-walled modal design, enables the cover plate to reciprocate axially at a specific excitation frequency, and drives the inclined specimen at an angle θ via a connector to achieve periodic contact and separation of the upper and lower friction pairs. The test process is controlled in a closed loop by a computer-control system-high-frequency vibration drive system-test device-sensor, achieving precise control of modal excitation application, dynamic response acquisition, and friction force calculation, ensuring that the test process is repeatable, controllable, and quantifiable, providing a reliable experimental platform for the study of friction-wear characteristics of wear-resistant materials under high-frequency vibration conditions.

[0048] like Figures 5-8 As shown, the main load-bearing structure of this invention is a circular loading frame with high overall stiffness and excellent vibration resistance. It can be divided into three parts: an upper interface area, a middle support rib area, and a lower flange base area. The design of this structure takes into account load-bearing capacity, modal response characteristics, and ease of assembly, aiming to achieve friction and wear testing under structural resonance conditions at specific frequencies.

[0049] 1) Lower part - flange base The lower flange base serves as the main installation and fixing body for this device. It has a flat, disc-shaped structure with multiple high-strength bolt holes evenly distributed along its edges, allowing for reliable connection to the loading equipment via bolts. This ensures the structural stability and operational safety of the system under high-frequency vibration conditions. This flange not only serves as the installation reference surface for the device but also provides constraint and support, offering a stable load-bearing foundation for the upper structure. A connecting groove is machined at the center of the upper part of the flange base for rapid positioning and assembly of the fixture. A force sensor is embedded within the connecting groove, enabling real-time measurement of the force acting on the sample contact interface during the test, achieving high-precision monitoring and data acquisition of the friction-wear process.

[0050] 2) Middle-support rib structure The central region is the core load-bearing and force-transmitting part of the device, employing a support rib structure to achieve lightweight design while meeting strength and stiffness requirements. A large area of ​​the central part of the main body is hollowed out, effectively reducing structural mass and vibration inertia, while improving overall dynamic response characteristics, enabling it to produce significant bending deformation under predetermined modes. Furthermore, a connecting groove is designed on the upper part of the base for assembling the sample connection mechanism and sensor components.

[0051] 3) Upper part – connection and positioning section The upper structure, serving as the functional interface area of ​​the test device, also features a ring of bolt holes 551 along its edge for assembly and connection with the upper cover plate, ensuring the overall rigidity and mechanical integrity of the device. The top also has assembly positioning holes 557 for precise coaxial positioning with the cover plate, ensuring the structure maintains symmetry and repeatability during vibration and loading, and preventing test deviations caused by assembly errors.

[0052] 4) Modal characteristics and structural optimization Modal optimization analysis was performed on the main frame during the design process to ensure that it exhibits modal characteristics of bending around the perimeter and reverse movement between the top and bottom surfaces in the middle at a specific frequency. By controlling the thickness, distribution, and perforation ratio of the support ribs, the upper surface is made to produce obvious axial up-and-down reciprocating motion at the target frequency, providing stable and repeatable dynamic loading conditions for frictional contact of the wear-resistant materials.

[0053] In summary, the main load-bearing structure of this invention, through the comprehensive application of support rib design, hollowing out for weight reduction, bolt connection and precise positioning structure, not only achieves stable operation under high frequency modal response, but also provides a solid structural foundation for the accuracy and repeatability of friction and wear tests.

[0054] The specific design concept of this invention is as follows: The main load-bearing structure of this invention follows the overall principles of "modal controllability, structural integration, rigid-flexible adaptation, and functional integration" in its design, aiming to achieve stable structural response and repeatable friction loading under high-frequency vibration conditions.

[0055] 1) Structural layout concept centered on modal response The design of the main load-bearing structure is centered on the target modal response. Finite element modal analysis is used to determine its structural morphology and wall thickness distribution, enabling it to exhibit typical modal characteristics of bending around the perimeter and reverse vibration at the top and bottom surfaces of the center at a specific frequency. This structural mode can induce periodic axial motion on the upper surface under resonant conditions, thereby driving the wear-resistant material to generate stable contact and friction loading, achieving a high degree of coupling between friction behavior and vibration modes.

[0056] 2) Overall configuration concept that emphasizes both integration and lightweighting To ensure structural stiffness and vibration consistency, the main body adopts an integrated molding design, avoiding assembly errors and loose connections that occur in split structures during high-frequency vibration. By introducing a hollowed-out design and supporting ribs in the central area, a balance is achieved between lightweighting and stiffness maintenance, which reduces structural inertia, improves vibration response sensitivity, and ensures the controllability and repeatability of the overall resonance frequency.

[0057] 3) Coordinated design of functional zoning and stress path Under the premise of structural integration, "implicit functional zoning" is carried out in different areas according to functional requirements: The bottom area primarily ensures a rigid connection between the structure and the shaking table; the middle area is the core of vibration response and force transmission, undertaking the main deformation and energy transfer; the top area is used to connect the loading cover plate and sensing devices, realizing an integrated transmission path for mechanical loading and signal acquisition. Furthermore, a connecting groove is provided at the center of the upper part of the flange base to facilitate subsequent fixture installation, and a force sensor is placed within the connecting groove to facilitate the measurement of the forces between the test sample interfaces during the experiment.

[0058] This partitioned design achieves the goal of "stiffness stratification and vibration coordination" in terms of stress and energy flow, enabling the structure to maintain continuous stress and stable response in a resonant state.

[0059] 4) Design concept combining modal control and frequency optimization During the design process, the natural frequencies and mode shapes of the structure are precisely controlled by adjusting the wall thickness gradient, the distribution of support ribs, and the proportion of openwork. This ensures that the target modal frequency is within the controllable range of the vibration table and that the deformation characteristics under this mode are most conducive to the occurrence and measurement of wear-resistant material contact friction. This "modal matching" design concept breaks through the limitations of traditional friction devices that rely solely on external mechanical loading, enabling the experiment to reproduce real friction behavior under high-frequency resonance conditions.

[0060] In summary, the main load-bearing structure design concept of this invention is based on modal driving, lightweight optimization, structural integration and functional integration, which realizes the unity of stable structural response and tribomechanical loading under high-frequency vibration conditions, and significantly improves the dynamic realism and measurement accuracy of friction and wear tests.

[0061] Design Principle: The main load-bearing structure of this invention adopts an integrated design concept. Its core lies in achieving a unified high rigidity, high stability, and multi-functional integration through structural integration and functional synergistic optimization. Compared with traditional split structures, this integrated frame eliminates errors and stress concentration problems caused by assembly interfaces, significantly improving the mechanical continuity and load transfer efficiency of the structure.

[0062] The structural design follows the basic principles of "function-oriented, continuous force flow, and controllable modes." First, the main load-bearing paths and key functional areas are determined based on the test conditions and functional requirements to ensure clear force transmission and reasonable force paths. Second, a frame layout with uniform stress distribution and controlled vibration response is achieved through topology optimization and finite element analysis. Finally, by adjusting the thickness of the support ribs, the distribution of the rib plates, and the proportion of openwork, the main body exhibits a characteristic mode of bending around the perimeter and reverse movement of the upper and lower surfaces in the center at the target frequency. This enables stable axial reciprocating motion under high-frequency vibration, providing repeatable and controllable dynamic loading conditions for frictional contact of wear-resistant materials.

[0063] Furthermore, a precision connection groove is installed in the central area of ​​the upper part of the flange base for mounting fixtures and embedding force sensors, enabling real-time measurement and signal transmission of friction interface loads, and ensuring the system's response accuracy and data reliability under high-frequency resonance conditions. The overall design principle fully embodies the deep coupling of structural mechanics, vibration control, and sensing measurement, providing a high-precision and highly stable structural foundation for friction-wear testing under high-frequency vibration conditions.

[0064] Cover plate and gasket: Cover plate 510: The cover plate of this invention has an integral disc-shaped structure and is a key component for realizing the connection and positioning functions of the device. This structure mainly consists of a main body plate, bolt holes, positioning holes, bosses, and connecting grooves.

[0065] The outer edge of the cover plate has several bolt holes for bolts to securely connect it to the lower main frame. Between the bolt holes are multiple locating holes, which, in conjunction with pins or locating pins, are used for precise circumferential positioning and coaxiality control during assembly, ensuring accurate spatial alignment between the cover plate and the main frame and preventing installation deviations and cumulative errors. Furthermore, a boss structure is provided on one side of the cover plate, with a connecting groove within it for connecting connectors, facilitating subsequent sample installation.

[0066] Gasket 520: The gasket of this invention is located between the main frame and the cover plate, serving as an intermediate component for achieving precise connection, mechanical transition, and overall modal control of the test device. By adjusting the number of gaskets, fine control of the modal response of the test device in a resonant state can be achieved, thereby obtaining reasonable frequency response characteristics. Figure 9 As shown). The first layer gasket 522 and the second layer gasket 523 are in a ring-shaped structure, with positioning holes and U-shaped grooves; the third layer gasket 524 ( Figure 10 As shown in the figure, a boss feature is added on this basis to enhance local stiffness and assembly reliability.

[0067] The gasket positioning holes 525 on the outer edge of the gasket mate with the corresponding holes on the main frame and the upper cover plate. Precise centering and circumferential positioning are achieved through pins or positioning pins, ensuring vertical and radial positional accuracy and effectively preventing assembly misalignment and connection deviations. The boss structure on the upper surface or outer edge not only provides local thickening to enhance compressive load-bearing capacity, but also forms a clear assembly interface, ensuring reliable fit and uniform stress distribution between the cover plate and the main frame.

[0068] Furthermore, the U-shaped groove 526 is arranged along the bolt connection path, providing installation space and a guiding channel for the bolts, ensuring smooth bolt insertion and fastening, while also buffering local assembly stress to prevent structural deformation or stress concentration caused by excessive pre-tightening. Overall, the gasket, through a triple design of "positioning—transition—buffering," achieves a high-precision connection between the upper cover plate and the main load-bearing structure, optimizes the assembly mechanical path and stress uniformity, and significantly improves the overall structural stability and connection reliability of the device.

[0069] Design Concept: The design of the cover plate and gasket in this invention follows the overall concept of "positioning—connection—transition—buffering," aiming to achieve structural stability, modal response consistency, and repeatability of sample contact conditions under high-frequency vibration loading. The cover plate achieves coordinated control of geometric constraints and mechanical fixation through positioning holes and bolt holes, while functional bosses and connecting grooves provide support for sample installation and ensure uniform force transmission. The gaskets achieve precise assembly, mechanical buffering, and stress dispersion through positioning holes, bosses, and U-shaped grooves, and their quantity can be adjusted to optimize the modal response under resonance conditions. The cover plate-gasket combination works in conjunction with the main frame support rib structure to form a high-precision, repeatable, and mechanically continuous device interface, providing reliable boundary conditions for the dynamic contact of wear-resistant material friction pairs under different angles and load conditions.

[0070] Design Principles: The design principles of the cover plate and gaskets in this invention are based on a comprehensive consideration of "precise positioning, mechanical transition, and modal compatibility." First, the cover plate achieves precise circumferential and radial alignment with the main frame through a combination of positioning holes and bolt holes, ensuring coaxiality and geometric accuracy during assembly. Simultaneously, the boss and connecting groove provide local thickening and force transmission paths, ensuring uniform stress on the sample and avoiding stress concentration. Second, the gaskets construct a transition and buffer structure through positioning holes, bosses, and U-shaped grooves, achieving mechanical continuity between the upper cover plate and the main frame. Furthermore, adjusting the number of gaskets optimizes the overall stiffness and resonant modal characteristics of the device, ensuring structural stability and consistent dynamic response under high-frequency vibration conditions. Finally, the cover plate-gasket combination works in conjunction with the main frame support rib structure, enabling the entire device to exhibit controlled bending and axial reciprocating motion under predetermined modes. This provides stable and repeatable boundary conditions for the dynamic contact of the wear-resistant material friction pair, achieving high-precision friction-wear testing.

[0071] Innovations: The innovations of the cover plate and gasket in this invention are reflected in three aspects: structural synergy, functional integration, and dynamic adjustability. First, the composite design of positioning holes, bosses, and bolt holes achieves high-precision positioning and reliable connection of the device, avoiding sample displacement or modal mismatch caused by assembly errors in traditional devices. Second, the gasket constructs a mechanical transition and buffering mechanism through bosses and U-grooves, effectively dispersing loads and reducing local stress concentration. Simultaneously, the overall structural stiffness and resonant modal characteristics can be precisely controlled by adjusting the number of gaskets, achieving modal matching and response optimization under high-frequency vibration conditions. Finally, the synergistic design of the cover plate-gasket combination and the main frame support rib structure ensures that the entire friction pair system maintains continuous force and modal compatibility under dynamic loading, providing stable, repeatable, and adjustable boundary conditions for friction-wear experiments of wear-resistant materials. These innovative designs significantly improve the accuracy, stability, and adaptability of the testing device, overcoming the limitations of existing friction and wear testing devices under high-frequency vibration.

[0072] Sample and connector: Specimen 540: The specimen designed in this invention has an overall prismatic structure, and its core feature is an inclined testing surface. This testing surface is not parallel to the bottom surface of the specimen, but forms a defined angle, denoted as θ. This angle is a key parameter in the specimen design, determining the degree of inclination of the testing surface. Furthermore, by adjusting the angle θ, a systematic assessment of the material's friction-wear behavior under different contact conditions can be achieved, thereby evaluating the material's wear resistance and frictional characteristics under different combinations of inclination angles and loads. Figure 11 and Figure 12 As shown.

[0073] In summary, this wedge-shaped specimen is designed to simulate the stress and frictional contact characteristics of materials or structures at a specific tilt angle. It can be used to test the frictional properties of wear-resistant materials under high-frequency vibration conditions, providing controllable and repeatable contact angle conditions for friction-wear experiments.

[0074] Assembly of the specimen and the connector: In this invention, the assembly sequence of the connector and the specimen from top to bottom is as follows: connector—specimen—specimen—connector (e.g., ... Figure 13 (As shown). During assembly, the connector is secured to the sample with bolts to achieve a firm connection. Both ends of the connector are embedded in the connecting grooves of the upper cover plate and the main frame, thus ensuring stability and stress continuity under vibration loading conditions.

[0075] This assembly method not only ensures that the sample is fixed in position and subjected to uniform force during high-frequency vibration, but also enables the contact surface of the friction pair to accurately reflect the stress state at the design angle θ. This design allows for reliable operation of the testing device under different vibration modes, guaranteeing the repeatability and accuracy of friction-wear data.

[0076] Design concept: The design of the specimen and connector in this invention follows the principles of adjustable friction angle, uniform mechanical force, vibration stability, and reliable assembly. The wedge-shaped specimen achieves systematic evaluation of friction-wear behavior under different contact conditions through an adjustable included angle θ. The connector is fastened with bolts and embedded in the grooves of the main frame and cover plate to ensure continuous and uniform force on the friction pair, maintain stability under high-frequency vibration conditions, and facilitate specimen replacement and angle adjustment through modular assembly, providing reliable and repeatable boundary conditions for high-frequency friction-wear experiments.

[0077] Design Principle: The design principle of the specimen and connector in this invention is based on the concepts of functional controllability, mechanical continuity, and modal compatibility. The wedge-shaped specimen controls the inclination of the friction contact surface through the included angle θ, realizing controllable loading under different contact conditions. The connector is fastened with bolts and embedded in the main frame and cover plate groove to form a continuous force path, ensuring that the friction pair is uniformly stressed and stable in position under high-frequency vibration conditions. At the same time, it is modally matched with the main bearing structure to ensure that the included angle of the friction surface and the stress state are consistent, achieving high precision and repeatability of the experiment. The modular design facilitates specimen replacement and angle adjustment.

[0078] Innovation: This invention forms a continuous force path by using an adjustable included angle θ of a wedge-shaped specimen and a bolt-fastened connection head, thereby achieving uniform force and stable position of the friction pair under high-frequency vibration and compatibility with the main body mode. The modular design facilitates specimen replacement and angle adjustment, thus improving the accuracy, repeatability and applicability of friction-wear testing.

[0079] Feasibility: The design of the specimen and connector in this invention is highly feasible and can be directly applied to high-frequency vibration friction-wear experiments. The wedge-shaped specimen allows for flexible adjustment of the friction contact surface through an adjustable included angle θ, enabling the selection of an appropriate angle according to different experimental conditions and systematically evaluating the wear resistance and friction characteristics of materials under different contact conditions. The connector is bolted into the connecting groove between the main frame and the cover plate, achieving stable fixation of the friction pair and continuous force transmission, ensuring accurate positioning and uniform stress on the friction surface under vibration loading. The modular design facilitates rapid specimen replacement and angle adjustment, improving experimental efficiency and repeatability. Furthermore, this design is compatible with high-frequency vibration conditions, and the angle and stress state of the friction pair can be maintained stably over a long period, resulting in highly reliable and repeatable experimental results. This provides an feasible and quantifiable technical solution for the systematic evaluation of the friction-wear performance of wear-resistant materials.

[0080] Overall Structure: The overall structure, from top to bottom, comprises a cover plate, gaskets, connectors, specimens, and a main frame. This structural design adheres to the principles of modal controllability, mechanical continuity, and functional integration, ensuring the device remains stable and reliable under high-frequency vibration conditions. The upper cover plate is secured to the gaskets and main frame with bolts and achieves precise coaxial alignment through positioning holes, ensuring stable position and consistent axial movement of the friction pair during vibration. The intermediate gaskets, acting as a mechanical transition and buffer layer, not only ensure uniform stress distribution but also effectively absorb local assembly stress, preventing micro-deformation caused by bolt pre-tightening. The connectors are embedded in the main load-bearing structure and cover plate grooves with bolts, achieving stable fixation and continuous force transmission of the friction pair, enabling the wedge-shaped specimen to exhibit controlled frictional contact behavior at an adjustable angle θ. The main load-bearing structure employs a support rib structure and a hollow design. The rationally distributed support ribs ensure overall rigidity and stability while achieving axial reciprocating motion of the upper cover plate at the target modal frequency, providing high-precision and repeatable dynamic loading conditions for friction-wear experiments on wear-resistant materials. Through the functional synergy of its components, the overall structure enables the device to operate reliably and produce highly consistent experimental results under high-frequency vibration and multi-angle contact conditions, providing a solid structural foundation for the performance evaluation of wear-resistant materials.

[0081] Design Concept: The overall structural design of this invention follows the principles of "modal controllability, functional integration, mechanical continuity, and modular convenience." The main frame, supporting ribs, and upper cover plate are optimized through modal analysis, enabling the structure to exhibit modal characteristics of bending around the perimeter and reverse movement of the upper and lower surfaces in the center at specific frequencies. This drives the sample to generate controllable axial reciprocating motion, achieving a high degree of coupling between the friction pair's force and vibration modes. The structure is functionally divided into an upper cover plate, a middle gasket and connector, the sample, and a lower main frame, achieving precise positioning, mechanical buffering, force transmission, and modal response assurance, ensuring uniform force and stable position of the friction pair under high-frequency vibration.

[0082] The main load-bearing structure adopts a thin-walled, hollow, and support rib layout design to achieve lightweight and rigid-flexible adaptability, improve vibration response sensitivity, and ensure axial movement stability of the upper cover plate. The modular design of each component facilitates quick assembly and disassembly, sample replacement, and angle adjustment, improving experimental efficiency and repeatability. The overall structure, through modal optimization, functional zoning, mechanical continuity, and modular design, provides a reliable structural foundation for high-precision, repeatable friction-wear experiments on wear-resistant materials.

[0083] Design Principles: The overall structural design follows the principles of "functional orientation, continuous force flow, modal compatibility, and modular integration" to achieve stability, accuracy, and repeatability in friction-wear experiments under high-frequency vibration. The structure is functionally divided into an upper cover plate, middle gaskets and connectors, the specimen, and a lower main frame, enabling continuous transmission of mechanical forces from the main frame to the friction pair. The cover plate ensures specimen positioning accuracy, the gaskets provide mechanical buffering and transition, the connectors securely fix the friction pair, and the main frame provides support and modal response, ensuring uniform force and positional stability of the friction pair during vibration.

[0084] By employing thin-walled, hollowed-out, and support rib designs, the natural frequencies and mode shapes of the structure are controlled, ensuring that the target modal frequencies remain within a controllable range. This allows for axial reciprocating motion of the upper cover plate under resonance conditions, providing stable and repeatable dynamic loading conditions for the friction pair. Modular component design ensures convenient assembly, disassembly, and sample replacement, while positioning holes, bosses, and bolt connections guarantee assembly precision and mechanical continuity. This ensures that the modal characteristics of the structure under high-frequency vibration and the friction test conditions remain intact, providing a reliable structural foundation for evaluating the performance of wear-resistant materials.

[0085] Innovation: This invention achieves dynamic loading of friction pairs under high-frequency resonance conditions through modal driving and structural optimization, enabling the experiment to highly replicate the friction-wear behavior under actual working conditions—a capability not found in traditional friction devices. The structure employs a thin-walled, hollow, and support rib layout, achieving a balance between lightweight design and rigidity-flexibility, improving vibration response sensitivity, and ensuring stable axial movement of the upper cover plate, providing controllable and repeatable loading conditions for the friction pairs.

[0086] Furthermore, the overall structure adopts a modular design, with the cover plate, gasket, connector, and sample forming a "positioning-connection-transition-buffering" structural system. High-precision positioning, mechanical continuity, and ease of assembly are achieved through bosses, positioning holes, bolt holes, and U-grooves, while ensuring modal compatibility and dynamic response stability. These innovations significantly improve the accuracy, reliability, and applicability of friction-wear testing, providing a scientific experimental method for the systematic evaluation of wear-resistant material properties.

[0087] Feasibility: The feasibility of the overall structure is reflected in its design, which fully considers the operability, repeatability, and reliability of high-frequency vibration friction-wear tests. Through modular design, the top cover, gaskets, connectors, and samples can be independently disassembled and assembled, enabling convenient sample replacement, angle adjustment, and device maintenance. At the same time, the positioning holes, bosses, and bolt connections ensure the assembly accuracy of the components, ensuring that the friction pair is stable in position and uniformly stressed during vibration.

[0088] The main frame adopts a thin-walled, hollow, and supporting rib layout, which reduces structural inertia while ensuring sufficient rigidity to achieve stable axial reciprocating motion of the upper cover plate. Guided by modal optimization analysis, the overall structure can generate the expected vibration mode at the target frequency, providing controllable and repeatable dynamic loading conditions for the friction pair. This design scheme balances mechanical performance, vibration response, and ease of operation, supporting high-precision, repeatable friction-wear experiments on wear-resistant materials, and possesses good engineering feasibility and experimental application value.

[0089] The method for calculating the friction force of the friction pair in this embodiment of the invention is as follows: In this apparatus, the upper and lower test surfaces of the friction pair are at an angle θ (5° to 30°) with the plane (bottom) of the cover plate. During the experiment, the entire apparatus is placed on a vibration loading platform, causing the support ribs to bend at a specific frequency, which in turn causes the cover plate to move up and down axially, driving the connector and the test sample to move synchronously, resulting in frictional contact between the upper and lower test surfaces.

[0090] A high-precision accelerometer is installed on the upper part of the cover plate to record the axial acceleration a(t) of the cover plate in real time. This is based on the effective mass m of the cover plate, the upper connector, and the upper part of the sample. eff Calculate the axial inertial force of the cover plate: F inertia (t)=m eff · a(t) Since there is an angle θ between the friction surface and the cover plate plane, the inertial force at the friction surface can be decomposed into: 1) Normal component (normal force): F N (t)=F inertia (t)· cosθ 2) Tangential component (along the friction surface direction): F tangential (t)=F inertia (t)· sinθ Friction force F f (t) Along the tangential direction of the friction surface, the maximum value is determined by the normal force and the coefficient of friction. Decide: F f (t)=μ·F N (t)=μ·F inertia (t)· cosθ Therefore, by adjusting the sample angle θ, the friction and wear behavior of materials under different contact conditions can be systematically assessed, enabling quantitative measurement of friction force and evaluation of wear resistance of friction pairs under high-frequency vibration conditions. This method ensures the repeatability and accuracy of experimental data and is applicable to friction performance studies under different friction pairs and sample geometric angles.

[0091] Furthermore, the force decomposition diagram of the present invention is as follows: Figure 14 As shown.

[0092] The above description is merely a specific embodiment of this application, but the scope of protection of this application is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in this application should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

Claims

1. An ultra-high frequency friction and wear testing device based on excitation response, characterized in that, include: A computer system, an experimental data acquisition and control system, and a high-frequency vibration drive system are connected in sequence, and a sensor system and an experimental device are installed on the high-frequency vibration drive system. The computer system serves as the core control and information processing unit of the entire test system, used to set vibration parameters, execute test control commands, monitor real-time signals, and perform subsequent data analysis. The test data acquisition and control system is used to receive multi-channel acceleration and displacement signals from the sensor system and to complete data acquisition and signal conversion. And according to the control commands issued by the computer system, the drive signal is output to the high-frequency vibration drive system according to the set control algorithm to realize closed-loop control of the test loading; The high-frequency vibration drive system is used to generate an excitation load of a specific frequency and amplitude according to the control signal issued by the test data acquisition and control system, and to apply dynamic energy to the test device so that the test device generates a controlled vibration response under structural modes. The main load-bearing structure of the test device is a cylindrical loading frame, which includes a lower flange base, a middle main load-bearing structure, and an upper connecting and positioning part. The middle main load-bearing structure adopts a hollowed-out cylindrical support rib structure, which is fixed to the lower flange base. The upper connecting and positioning part includes a cover plate, which is fixed to the top opening of the support rib structure. The test device also includes a first connector, a second connector, an upper sample, and a lower sample. A first connecting groove is formed in the center of the inner wall of the cover plate, and a second connecting groove is formed in the center of the lower flange base. The upper sample is fixed to the first connector, which is fixedly installed in the first connecting groove. The lower sample is fixed to the second connector, which is fixedly installed in the second connecting groove, so that the upper sample and the lower sample are in contact with each other to form a friction pair. The upper and lower specimens have the same structure, both adopting a wedge-shaped oblique truncated quadrangular prism structure, so that the oblique section of the oblique truncated quadrangular prism structure forms an adjustable angle θ with the bottom surface, and the oblique sections of the upper and lower specimens are in contact with each other as the test surfaces.

2. The ultra-high frequency friction and wear testing device based on excitation response according to claim 1, characterized in that, The sensor system includes an acceleration sensor, a displacement sensor, and a force sensor. An acceleration sensor is installed on the top of the high-frequency vibration drive system, and an acceleration sensor and a displacement sensor are installed on the top of the test device. The force sensor is arranged in the second connecting groove.

3. The ultra-high frequency friction and wear testing device based on excitation response according to claim 1, characterized in that, The lower flange base is in the shape of a flat disc and is fixed to the high-frequency vibration drive system by bolts, providing a stable installation reference and constraint for the test device in the resonant state.

4. The ultra-high frequency friction and wear testing device based on excitation response according to claim 1, characterized in that, The cover plate is a disc structure with bolt holes and positioning holes arranged on its outer edge for fixing to the top opening of the supporting rib structure. It also has a boss and the first connecting groove on its surface for fixing to the first connector and the upper sample, thereby achieving geometric positioning and mechanical load transfer.

5. The ultra-high frequency friction and wear testing device based on excitation response according to claim 1, characterized in that, The test apparatus also includes a gasket located between the cover plate and the top opening of the support rib structure.

6. The ultra-high frequency friction and wear testing device based on excitation response according to claim 5, characterized in that, The gasket includes a first gasket, a second gasket, and a third gasket. The first and second gaskets are in a ring shape and have positioning holes and U-shaped grooves. The third gasket has positioning holes, U-shaped grooves, and bosses.

7. The ultra-high frequency friction and wear testing device based on excitation response according to claim 1, characterized in that, The upper sample is fastened to the first connector, and the lower sample is fastened to the second connector using bolts.

8. The ultra-high frequency friction and wear testing device based on excitation response according to claim 1, characterized in that, The support rib structure adopts a thin-walled modal design with a wall thickness of 5mm to 10mm, so that the support rib structure exhibits a modal characteristic of bending around the four sides at a specific frequency.

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