An elastic supporting platform for overall vibration test of mine electric motor

Abstract

This invention relates to the field of elastic support platforms, specifically an elastic support platform for whole-machine vibration testing of a mining electric motor. It includes an upper test bearing plate, a vibration intelligent sensor on one side of the upper test bearing plate, and a test platform base on the lower side of the upper test bearing plate. A positive conical spring and a negative conical spring are mirror-imagely positioned between the upper test bearing plate and the test platform base. An adjusting sleeve is provided between the positive and negative conical springs, and a test vibration damping adjustment unit is located within the adjusting sleeve. A mounting hole is located on the lower side of the upper test bearing plate, and a non-self-locking ball screw shaft is installed within the mounting hole, with the adjusting sleeve passing through the ball screw shaft. The ball screw shaft drives the test vibration damping adjustment unit to unload force, achieving adaptive adjustment of support stiffness according to vibration load. This avoids resonance at the motor's operating excitation frequency and accurately converts axial vibration into rotational motion to generate adaptive damping unloading, improving the platform's adaptability to various operating conditions.

Description

Technical Field

[0001] This invention relates to the field of elastic support platforms, specifically an elastic support platform for whole-machine vibration testing of mining electric motors. Background Technology

[0002] The elastic support platform for whole-machine vibration testing of mining electric motors is an indispensable core tooling for performance testing of explosion-proof mining motors. It is widely used in the factory inspection and type testing of various explosion-proof motors in coal mines. Its structural design and modal control accuracy directly determine the authenticity and compliance of vibration test data, avoiding data distortion and missed fault detection. High-end mining motors such as high-voltage, high-power, and frequency converter integrated machines have more stringent requirements for modal stability and explosion-proof safety. Traditional devices can no longer meet the rigid requirements of safe production and certification testing.

[0003] To address the aforementioned issues, existing technologies offer several solutions. For instance, patent application CN202423314464.8 discloses a vibration test bench for electromechanical equipment. This application outlines the following solution: the test bench incorporates a fixed base, a vibration table, a double-spring buffer, and a three-way X / Y / Z clamping mechanism. A vibration motor provides the excitation source, and a bidirectional screw drives the clamping plate for multi-directional clamping. A locking pressure plate further tightens the top, improving test stability and preventing equipment from falling and being damaged. However, this solution has limitations in practical application: the fixed stiffness of the double-spring buffer structure prevents adjustment of the system's natural frequency. When replacing different specifications of mining motors, the system's natural frequency easily coincides with the motor's operating excitation frequency, triggering severe resonance. The fixed damper alone cannot effectively suppress the resonance amplitude, failing to meet national standard compliance requirements and potentially causing damage to the tested motor structure and fatigue damage to equipment components. Summary of the Invention

[0004] The purpose of this invention is to provide an elastic support platform for whole-machine vibration testing of mining electric motors, so as to solve the problem of test data distortion and the problem of resonance that easily occurs in existing tests.

[0005] To solve the above-mentioned technical problems, the purpose of this invention is to provide an elastic support platform for whole-machine vibration testing of mining electric motors.

[0006] This invention discloses an elastic support platform for whole-machine vibration testing of a mining electric motor, comprising an upper test bearing plate, a vibration intelligent sensor disposed on one side of the upper test bearing plate, a test platform base disposed on the lower side of the upper test bearing plate, a positive conical spring and a negative conical spring mirror-arranged between the upper test bearing plate and the test platform base, the positive conical spring being supported on the upper test bearing plate and the negative conical spring being supported on the test platform base, and an adjusting sleeve disposed between the positive conical spring and the negative conical spring, the adjusting sleeve having positioning countersunk holes at both axial ends. The small-diameter ends of the positive and negative conical springs are respectively encased in the positioning countersunk holes. A test vibration damping adjustment unit is provided inside the adjusting sleeve. A mounting hole is provided on the lower side of the upper test bearing plate. A ball screw shaft is provided in the mounting hole. The ball screw shaft is non-self-locking. The ball screw shaft passes through the adjusting sleeve along the axis of the positive conical spring. The ball screw shaft drives the test vibration damping adjustment unit to unload force. The test platform base is provided with a guide sliding hole that is aligned with the position of the ball screw shaft. The guide sliding hole slides in conjunction with the ball screw shaft.

[0007] Furthermore, using an upper test support plate equipped with a vibration intelligent sensor and a test platform base as the basic support structure, a positive conical spring and a negative conical spring are mirror-mounted between the upper test support plate and the test platform base. The positive conical spring is supported on the upper test support plate, and the negative conical spring is supported on the test platform base. An adjusting sleeve with positioning countersunk holes at both ends and an internal test vibration damping adjustment unit is set between the two sets of springs. The small diameter ends of the positive and negative conical springs are respectively covered in the corresponding positioning countersunk holes. At the same time, a non-self-locking ball screw shaft is set in the mounting hole on the lower side of the upper test support plate. The ball screw shaft passes through the adjusting sleeve along the axis of the positive conical spring and can drive the test vibration damping adjustment unit to complete the force unloading action. It forms a sliding engagement with the ball screw shaft in the guide sliding hole on the test platform base corresponding to the position of the ball screw shaft. The overall structural design enables the support system stiffness to adaptively adjust according to the vibration load of the tested mining motor, effectively avoiding the motor's operating excitation frequency and suppressing resonance at its source. Simultaneously, it precisely converts the axial vibration displacement generated by the motor into rotational motion, driving the test vibration damping adjustment unit to generate adaptive damping force to achieve vibration unloading and amplitude suppression. This avoids vibration impact interfering with test results and ensures the authenticity and accuracy of data collected by the intelligent vibration sensor. Furthermore, the positioning countersunk holes achieve precise coaxial positioning of the two sets of conical springs, preventing spring failure due to uneven load. Guide sliding holes ensure the smoothness and transmission accuracy of the ball screw shaft's axial sliding, significantly improving the test platform's operational stability and adaptability to various working conditions. This solves the problems of traditional mining motor vibration test benches with fixed stiffness structures easily triggering resonance and having poor damping unloading effects.

[0008] Preferably, the test vibration damping adjustment unit includes a damping medium cavity and a rotating damping adjustment flywheel. The damping medium cavity is provided inside the adjustment sleeve and is filled with viscous damping fluid. The rotating damping adjustment flywheel is rotatably arranged inside the damping medium cavity and is completely immersed in the viscous damping fluid. The rotating damping adjustment flywheel and the ball screw shaft are connected by a helical transmission through balls. Damping adjustment blades are provided on the outer circumference of the rotating damping adjustment flywheel. The ball screw shaft drives the rotating damping adjustment flywheel to rotate inside the damping medium cavity with the vertical displacement of the upper test bearing plate.

[0009] Furthermore, by setting a damping medium cavity within the adjusting sleeve and filling it with viscous damping fluid, a rotating damping adjusting flywheel is rotatably installed within the damping medium cavity and completely submerged in the viscous damping fluid. The rotating damping adjusting flywheel and the ball screw shaft are connected via a helical transmission through the balls. Simultaneously, damping adjusting blades are set on the outer circumference of the rotating damping adjusting flywheel. This achieves a transmission structure where the ball screw shaft, following the vertical displacement of the upper test bearing plate, drives the rotating damping adjusting flywheel to rotate within the damping medium cavity. This efficiently and accurately converts the axial vibration displacement generated by the tested mining motor into the rotational motion of the rotating damping adjusting flywheel. The shear damping force generated by the rotating damping adjusting flywheel driving the damping adjusting blades to rotate in the viscous damping fluid forms a vibration... The adaptive damping unloading effect with real-time dynamic amplitude matching can quickly establish damping force and suppress resonance peaks when the motor starts and stops and passes through the resonance zone, avoiding the transmission of vibration impact to the upper test bearing plate and interfering with the test results. It effectively ensures the authenticity and compliance of the data collected by the vibration intelligent sensor. At the same time, the ball screw drive ensures the response speed and transmission efficiency of the vibration to rotational motion conversion. The non-locking transmission characteristic avoids the risk of jamming failure. The setting of the rotating damping adjustment flywheel being completely immersed in viscous damping fluid ensures the continuity and stability of damping force output. It can adapt to the vibration test requirements of mining motors with different power and different excitation frequencies, and solves the pain points of fixed damping structure of test bench, such as non-adjustable damping force, poor wideband vibration adaptability, insufficient resonance suppression capability, and easy distortion of test data.

[0010] Preferably, each of the plurality of damping adjustment blades is provided with a medium flow adjustment hole, and the medium flow adjustment hole penetrates the damping adjustment blade.

[0011] Furthermore, by opening medium flow adjustment holes through both sides of the damping adjustment blades on the rotating damping adjustment flywheel, the vertical displacement of the upper test bearing plate drives the ball screw shaft, driving the rotating damping adjustment flywheel to rotate within the damping medium cavity filled with viscous damping fluid. This allows the damping fluid to pass through the medium flow adjustment holes, forming a bidirectional free flow. This breaks the smooth laminar boundary layer formed on the surface of the damping adjustment blades during rotation and the eddy dead zone on the back of the damping adjustment blades, generating a dual effect of strong turbulence and throttling damping. An additional damping and force relief path is added on top of the original shear damping of the damping adjustment blades, significantly improving the overall damping force at the same speed. This particularly enhances the damping effect of the mining motor during low-speed rotation in the resonance zone during start-up and shutdown, while simultaneously eliminating rotational resistance. The damping adjustment flywheel addresses the damping force lag issue during the reciprocating forward and reverse rotation of vibration, achieving stable force relief throughout the entire vibration stroke and cycle. It also drives forced convection of the damping fluid within the damping medium cavity, evenly dispersing the localized heat generated by the shearing of the damping adjustment blades throughout the entire cavity. This further enhances the resonance suppression capability and force relief effect of the test vibration damping adjustment unit, more efficiently preventing vibration impact from being transmitted to the upper test bearing plate and interfering with test results. It ensures the authenticity and compliance of the data collected by the vibration intelligent sensor, while reducing the alternating fluid resistance impact on the damping adjustment blades, balancing the circumferential and axial internal pressures of the damping medium cavity, preventing damping fluid accumulation on an off-center basis, and improving the long-term operational reliability of the test vibration damping adjustment unit and its adaptability to non-horizontal installation conditions in mining sites.

[0012] Preferably, a medium flow adjustment gap is provided between the damping adjustment blade and the damping medium cavity, and the medium flow adjustment gap is 1.5mm to 2mm.

[0013] Furthermore, by designing a 1.5mm to 2mm media flow adjustment gap between the damping adjustment blade and the inner wall of the damping medium cavity, this gap can prevent motion interference and scraping jamming between the damping adjustment blade and the inner wall of the damping medium cavity during high-speed rotation and forward / reverse switching of the rotary damping adjustment flywheel. This ensures the smoothness and transmission stability of the rotary damping adjustment flywheel driven by the ball screw shaft. It also controls the shear layer thickness of the viscous damping fluid, forming a stable and linearly adjustable shear damping force, thus avoiding the damping shear effect caused by an excessively large gap. This addresses issues such as insufficient damping efficiency, poor resonance suppression, and excessively small gaps leading to overloaded damping force and rapid local shear temperature rise of the damping fluid. Furthermore, it can be combined with through-hole medium flow regulation holes on the damping adjustment blades to guide the damping fluid into a stable and controllable flow field during blade rotation, further enhancing turbulent damping effects, improving overall damping unloading efficiency, effectively ensuring the authenticity of data collected by the vibration intelligent sensor, and reducing operating noise and component wear caused by hard contact between the damping adjustment blades and the cavity, thus improving the long-term operational reliability and service life of the testing platform.

[0014] Preferably, a ball joint seat is provided at the upper end of the ball screw shaft, a spherical groove is provided in the mounting hole, the ball joint seat is installed in the spherical groove, the spherical groove and the ball joint seat are spaced 1mm to 1.5mm apart, and when the positive conical spring is not compressed, the spherical groove and the ball joint seat maintain surface contact.

[0015] Furthermore, a spherical groove is set in the mounting hole on the lower side of the upper test bearing plate, and a ball joint seat is set on the upper end of the ball screw shaft used to drive the test vibration damping adjustment unit to unload the force. The ball joint seat is adapted to be installed in the spherical groove. At the same time, a fit clearance of 1mm to 1.5mm is set between the spherical groove and the ball joint seat, and the spherical groove and the ball joint seat are limited to maintain surface contact when the positive conical spring is not compressed. This realizes the adaptive spherical hinge fit between the ball screw shaft and the upper test bearing plate. It can compensate for the clamping off-center load, installation coaxiality error and radial runout generated during vibration of the tested mining motor in real time. It avoids the ball screw shaft from bending or jamming due to additional radial load, and ensures that the ball screw shaft slides smoothly only in the axial direction. It accurately transmits the real axial vibration displacement and axial displacement jitter of the tested motor, and ensures the purity of the axial displacement jitter test data. Among them, 1mm to 1mm The 0.5mm gap range provides ample room for the self-aligning of the ball joint seat and limits the radial runout of the ball screw shaft, avoiding unstable damping force output and nonlinear distortion of axial displacement jitter transmission caused by transmission path deviation. This ensures linear and accurate transmission of axial displacement jitter throughout the entire stroke. When the conical spring is not compressed, the spherical groove contacts the ball joint seat, ensuring the coaxial positioning accuracy of the ball screw shaft during initial installation. It also provides suitable room for the ball joint seat when the motor is under load and the spring is compressed, ensuring distortion-free transmission of vibration throughout the entire test cycle. This guarantees efficient and accurate conversion of axial vibration displacement into the rotational motion of the test vibration damping adjustment unit, enhances the adaptive damping unloading and resonance suppression effects, ensures the authenticity of axial displacement jitter test data, and significantly improves the operational stability and adaptability of the test platform.

[0016] Preferably, a rubber layer is provided between the mounting hole and the ball screw shaft, the thickness of the rubber layer being 1mm to 1.5mm, and a hollow cylindrical rubber sleeve is provided between the hole wall of the guide slide hole and the ball screw shaft.

[0017] Furthermore, by setting a rubber layer with a thickness of 1mm to 1.5mm between the mounting hole and the corresponding ball screw shaft, and simultaneously setting a hollow rubber sleeve at both ends of the guide slide hole wall and the ball screw shaft, a progressive optimization is achieved based on the spherical fit between the ball joint seat and the spherical groove to realize the self-aligning structure of the ball screw shaft. The precise rubber layer thickness of 1mm to 1.5mm provides sufficient elastic buffer margin for the fit between the ball screw shaft and the mounting hole, effectively isolating the radial vibration generated during the operation of the tested mining motor, compensating for clamping off-center load and installation coaxiality errors, and avoiding vibration transmission path deviation and axial vibration transmission distortion caused by excessively thick rubber layer, as well as insufficient vibration isolation and buffering effect and hard contact wear caused by excessively thin rubber layer. The hollow rubber sleeve in the guide slide hole can utilize the controllable radial deformation formed by its hollow structure. This device is capable of handling minute radial runout during the axial reciprocating sliding of the ball screw shaft. It forms a symmetrical radial vibration isolation system with the rubber layer inside the mounting hole, and simultaneously provides double self-aligning protection with the self-aligning structure of the ball joint seat. This avoids the risk of bending, jamming, and abnormal wear caused by additional radial loads on both ends of the ball screw shaft. It accurately and stably transmits the axial vibration displacement generated by the tested motor to the test vibration damping adjustment unit, further enhancing the adaptive damping and resonance suppression effect of the unit. This prevents test data deviations caused by screw jamming, vibration transmission distortion, and damping force output fluctuations. Furthermore, the high elasticity and vibration absorption characteristics of the rubber layer and hollow rubber sleeve reduce operating noise and impact wear between metal parts during the ball screw shaft sliding process, significantly improving the long-term operational reliability, adaptability to mining conditions, and overall service life of the testing platform.

[0018] Preferably, the openings of the adjusting sleeve through which the ball screw shaft passes are provided with sealing rings.

[0019] Furthermore, by installing sealing rings at the openings of the adjusting sleeve through which the ball screw shaft passes, a strong synergistic effect is achieved with the core structure of the test vibration damping adjustment unit. The bidirectional seal completely blocks the opening gaps at both ends of the adjusting sleeve through which the ball screw shaft passes. This prevents leakage of the viscous damping fluid during the rotation and stirring of the rotary damping adjusting flywheel and the axial reciprocating sliding of the ball screw shaft with vibration. It avoids problems such as damping force attenuation and failure of force relief and vibration reduction effects due to damping fluid loss and liquid level drop, ensuring a clean and stable working environment inside the damping medium cavity and ensuring the rotation of the rotary damping adjusting flywheel. The shear damping force can be continuously, stably, and linearly output, further enhancing the adaptive unloading and vibration reduction and resonance peak suppression effect of the test vibration damping adjustment unit. This avoids axial vibration transmission distortion and test data deviation caused by damping force fluctuations and transmission jamming, effectively ensuring the authenticity of the vibration test data of the entire mining motor collected by the vibration intelligent sensor. At the same time, it can significantly reduce the abnormal wear of the moving parts inside the test vibration damping adjustment unit, extend the maintenance cycle and overall service life of the device, and improve the long-term operational reliability and adaptability of the test platform under complex mining field conditions.

[0020] Preferably, the outer surface of the adjusting sleeve is provided with multiple circumferentially distributed damping unit heat dissipation fins.

[0021] Furthermore, by setting multiple circumferentially distributed damping unit heat dissipation fins on the outer surface of the regulating sleeve, the heat exchange contact area between the regulating sleeve and the outside air is significantly increased. This accelerates the outward conduction and convective heat dissipation efficiency of the large amount of working heat generated by the high-speed rotation of the rotating damping regulating flywheel, the continuous shearing of the damping regulating blades, and the throttling and turbulent flow of the medium flow regulating hole in the damping medium cavity. This fundamentally suppresses the problems of viscosity decrease, damping force attenuation, and failure of force unloading and vibration reduction effect caused by excessively high continuous working temperature of the damping fluid. It ensures that the damping force remains stable and linear during the continuous batch testing of mining motors. At the same time, it can work in conjunction with the medium flow regulating hole of the damping regulating blades to drive the damping. The forced convection formed by the liquid achieves a dual heat dissipation effect: uniform heat diffusion inside the damping medium cavity and rapid heat dissipation from the external fins. This further enhances the overall heat dissipation capacity, prevents local overheating and aging of the damping liquid, and extends the service life of the damping liquid and the maintenance cycle of the device. In addition, the circumferentially distributed fin structure can also simultaneously enhance the overall structural strength of the adjusting sleeve, preventing deformation caused by the reciprocating compression of the adjusting sleeve by the positive and negative conical springs. This ensures the coaxial positioning accuracy of the two sets of conical springs and the sealing performance of the damping medium cavity, effectively guaranteeing the authenticity of the vibration test data of the entire mining motor collected by the vibration intelligent sensor. It also significantly improves the long-term operational reliability, continuous working capability, and adaptability of the testing platform to high-load and harsh working conditions in mining sites.

[0022] Preferably, the outer spherical surface of the ball joint seat and the inner spherical surface of the spherical groove are both provided with a wear-resistant polytetrafluoroethylene coating, and the thickness of the coating is 0.2mm to 0.5mm.

[0023] Furthermore, a wear-resistant polytetrafluoroethylene (PTFE) coating with a thickness of 0.2mm to 0.5mm is applied to both the outer spherical surface of the ball joint seat and the inner spherical surface of the corresponding mating spherical groove. The 0.2mm to 0.5mm coating thickness ensures sufficient wear resistance and protective performance without affecting the mating clearance between the spherical groove and the ball joint seat, or the initial positioning accuracy and self-aligning movement allowance of the ball joint structure due to excessive thickness. Conversely, an excessively thin coating will not result in insufficient wear protection or rapid wear failure after long-term use. The PTFE coating, with its low coefficient of friction, high wear resistance, and self-lubricating properties, significantly reduces the sliding friction resistance between the ball joint seat and the mating spherical surface of the spherical groove. This prevents dry friction, jamming, and abnormal noise during high-frequency vibration and reciprocating oscillation self-aligning, ensuring smooth and stable self-aligning of the ball joint structure throughout the process. It also provides real-time compensation for the off-center loading and installation of the tested mining motor. The system addresses coaxiality errors and radial runout generated during vibration, fundamentally mitigating the risks of bending, jamming, and abnormal wear of the ball screw shaft due to additional radial loads. It also significantly improves the long-term wear resistance and service life of the ball joint structure, preventing wear on the spherical mating surface after prolonged high-frequency use, which can lead to excessive clearance, decreased self-aligning accuracy, and deviation of the screw transmission path. This ensures the ball screw shaft always slides smoothly along the axial direction without jamming, accurately and stably transmitting the axial vibration displacement generated by the tested motor to the test vibration damping adjustment unit. This further enhances the adaptive damping and resonance suppression effects of the test vibration damping adjustment unit, preventing test data deviations caused by screw jamming, vibration transmission distortion, and damping force output fluctuations. Furthermore, it works in conjunction with the rubber layer in the mounting hole and the hollow rubber sleeve in the guide slide hole to form full-stroke radial protection, further improving the running stability of the ball screw shaft and its adaptability to harsh working conditions such as high dust and high loads in mining.

[0024] By means of the above-described solution, the present invention has at least the following advantages:

[0025] 1. By adopting an upper and lower bearing structure equipped with a vibration intelligent sensor, positive and negative conical springs are mirrored between the upper test bearing plate and the test platform base and coaxially positioned by the adjusting sleeve. Combined with a non-self-locking ball screw shaft that runs through the shaft and a rotating damping adjustment flywheel test vibration damping adjustment unit, the support stiffness can be adaptively adjusted according to the vibration load, avoiding resonance from the motor's operating excitation frequency at the source. It can also accurately convert axial vibration into rotational motion to generate adaptive damping unloading, ensuring the authenticity and accuracy of test data and improving the platform's adaptability to working conditions.

[0026] 2. By setting damping adjustment blades with through-medium flow adjustment holes on the outside of the rotating damping adjustment flywheel and limiting the medium flow adjustment gap to 1.5mm to 2mm, and adding circumferential damping unit heat dissipation fins on the outer surface of the adjustment sleeve, the laminar boundary layer is broken to form turbulent flow and throttling dual damping, which enhances the peak suppression effect of the resonance zone during start-stop. At the same time, the working heat of the damping fluid can be quickly dissipated to avoid the damping force attenuation caused by temperature rise, and ensure stable and linear damping output during continuous testing.

[0027] 3. By setting a ball joint seat with PTFE coating at the upper end of the ball screw shaft and reserving a self-aligning clearance of 1mm to 1.5mm, and with the upper and lower rubber vibration isolation layers and the bidirectional sealing ring of the adjusting sleeve, it can not only compensate for the clamping load and radial runout in real time, avoid the screw bending and jamming, but also isolate radial vibration, prevent damping fluid leakage, extend the service life of core components, and adapt to the complex and harsh working conditions of mining.

[0028] The above description is merely an overview of the technical solution of the present invention. In order to better understand the technical means of the present invention and to implement it in accordance with the contents of the specification, the preferred embodiments of the present invention are described in detail below with reference to the accompanying drawings. Attached Figure Description

[0029] To more clearly illustrate the technical solutions of the embodiments of the present invention, the accompanying drawings used in the embodiments will be briefly introduced below. It should be understood that the following drawings only show a certain embodiment of the present invention and should not be regarded as a limitation on the scope. For those skilled in the art, other related drawings can be obtained based on these drawings without creative effort.

[0030] Figure 1 This is a schematic diagram of the structure of the elastic support platform for whole-machine vibration testing of the mining electric motor of the present invention; Figure 2 This is a front view of the elastic support platform for whole-machine vibration testing of the mining electric motor of the present invention; Figure 3 yes Figure 2 Sectional view of AA; Figure 4 yes Figure 3 Enlarged view of point B in the middle; Figure 5 yes Figure 3 Enlarged view of point C in the middle; Figure 6 This is a schematic diagram of the rotating damping adjustment flywheel.

[0031] In the diagram: 1. Upper test bearing plate; 101. Mounting hole; 102. Spherical groove; 103. Rubber layer; 104. Inner spherical surface; 2. Vibration intelligent sensor; 3. Test platform base; 301. Guide sliding hole; 302. Rubber sleeve; 4. Positive conical spring; 5. Reverse conical spring; 6. Adjusting sleeve; 601. Positioning countersunk hole; 602. Damping medium cavity; 603. Medium flow adjustment gap; 604. Sealing ring; 605. Damping unit heat dissipation fins; 7. Ball screw shaft; 701. Ball joint seat; 702. Outer spherical surface; 8. Rotary damping adjustment flywheel; 801. Damping adjustment blade; 802. Medium flow adjustment hole; 9. Motor; 10. Fixing device. Detailed Implementation

[0032] The specific embodiments of the present invention will be described in further detail below with reference to the accompanying drawings and examples. The following examples are for illustrative purposes only and are not intended to limit the scope of the invention.

[0033] See Figures 1 to 6A preferred embodiment of the present invention provides an elastic support platform for whole-machine vibration testing of a mining electric motor, comprising an upper test bearing plate 1, a fixing device 10 disposed at the upper end of the upper test bearing plate 1, a motor 9 disposed between the fixing devices 10, a vibration intelligent sensor 2 disposed on one side of the upper test bearing plate 1, a test platform base 3 disposed on the lower side of the upper test bearing plate 1, a positive conical spring 4 and a negative conical spring 5 mirror-arranged between the upper test bearing plate 1 and the test platform base 3, the positive conical spring 4 being supported on the upper test bearing plate 1, and the negative conical spring 5 being supported on the test platform base 3, and an adjusting sleeve 6 disposed between the positive conical spring 4 and the negative conical spring 5, the outer surface of the adjusting sleeve 6 being provided with multiple The damping unit has heat dissipation fins 605 distributed circumferentially. The adjusting sleeve 6 has positioning countersunk holes 601 at both axial ends. The small-diameter ends of the positive conical spring 4 and the negative conical spring 5 are respectively encased in the positioning countersunk holes 601. The adjusting sleeve 6 contains a test vibration damping adjustment unit, which includes a damping medium cavity 602 and a rotating damping adjustment flywheel 8. The damping medium cavity 602 is filled with viscous damping fluid. The rotating damping adjustment flywheel 8 is rotatably mounted within the damping medium cavity 602 and is completely submerged in the viscous damping fluid. The upper test bearing plate 1 has mounting holes 101 on its lower side. A ball screw shaft 7 is installed inside the mounting hole 101. A rubber layer 103 with a thickness of 1.5mm is provided between the mounting hole 101 and the ball screw shaft 7. A ball joint seat 701 is provided at the upper end of the ball screw shaft 7. A spherical groove 102 is provided in the mounting hole 101. The ball joint seat 701 is installed in the spherical groove 102. The spherical groove 102 and the ball joint seat 701 are spaced 1.5mm apart. When the conical spring 4 is not compressed, the spherical groove 102 and the ball joint seat 701 maintain surface contact. The outer spherical surface 702 of the ball joint seat 701 and the inner spherical surface 104 of the spherical groove 102 are both coated with wear-resistant polytetrafluoroethylene coating with a thickness of 0.2mm. The ball screw shaft 7 is a non-self-locking type. The rod shaft 7 passes through the adjusting sleeve 6 along the axis of the conical spring 4, and the openings of the adjusting sleeve 6 through which the ball screw shaft 7 passes are all equipped with sealing rings 604. The ball screw shaft 7 drives the test vibration damping adjustment unit to unload the force. The rotating damping adjustment flywheel 8 and the ball screw shaft 7 form a helical transmission cooperation through the balls. The outer circumference of the rotating damping adjustment flywheel 8 is provided with damping adjustment blades 801. Each of the multiple damping adjustment blades 801 is provided with a medium flow adjustment hole 802. The medium flow adjustment hole 802 passes through the damping adjustment blade 801. A medium flow adjustment gap 603 is provided between the damping adjustment blade 801 and the damping medium cavity 602. The medium flow adjustment gap 603 is 1.The ball screw shaft 7, with a diameter of 5mm, rotates within the damping medium cavity 602 as the upper test bearing plate 1 moves vertically. The test platform base 3 has a guide hole 301 aligned with the position of the ball screw shaft 7. The guide hole 301 slides within the ball screw shaft 7, and a hollow cylindrical rubber sleeve 302 is positioned between the guide hole 301 and the ball screw shaft 7.

[0034] The working principle of this invention is as follows: refer to Figures 1 to 6 Before the vibration test of the entire mining motor, the motor 9 to be tested is first fastened to the upper end face of the upper test bearing plate 1 by the fixing device 10. At this time, the upper test bearing plate 1 is subjected to the downward vertical displacement of the motor 9, which causes the positive conical spring 4 to be compressed and contracted. The small diameter end of the positive conical spring 4 pushes the adjusting sleeve 6 to move downward, and simultaneously compresses the reverse conical spring 5. The positive and reverse conical springs achieve coaxial top support through the positioning countersunk holes 601 at both ends of the adjusting sleeve 6, forming the initial support stiffness. The ball screw shaft 7 slides down synchronously with the upper test bearing plate 1, and its lower end moves down smoothly along the guide sliding hole 301 of the test platform base 3. The ball joint seat 701 maintains the initial contact state in the spherical groove 102, completing the static preloading and initial stiffness establishment of the test platform.

[0035] When the tested motor 9 starts running and generates axial vibration, the upper test bearing plate 1 moves vertically up and down with the vibration, causing the positive conical spring 4 and the negative conical spring 5 to undergo alternating compression and rebound deformation. Since the positive and negative conical springs are arranged in a mirror-image top-down manner and their stiffness changes nonlinearly with the amount of compression, when the vibration load increases, the spring compression increases and the support stiffness increases synchronously. When the vibration load decreases, the spring rebounds and the support stiffness decreases synchronously. This achieves real-time adaptive adjustment of the support system stiffness according to the vibration load of the motor 9, so that the system's natural frequency always avoids the operating excitation frequency of the motor 9, suppressing the occurrence of resonance phenomenon from the root and avoiding interference of resonance peaks with test data and equipment damage.

[0036] Meanwhile, the vertical reciprocating displacement of the upper test bearing plate 1 drives the ball screw shaft 7 to slide synchronously along the axial direction. Since the ball screw shaft 7 adopts a non-self-locking design, it forms an efficient helical transmission with the rotary damping adjustment flywheel 8 through the balls, which accurately converts the axial linear motion of the ball screw shaft 7 into the high-speed rotational motion of the rotary damping adjustment flywheel 8 in the damping medium cavity 602. The damping adjustment blade 801 on the outside of the rotary damping adjustment flywheel 8 rotates synchronously with it, generating shear damping force in the fully immersed viscous damping liquid. The medium flow adjustment hole 802 through the damping adjustment blade 801 breaks the laminar boundary layer and eddy dead zone formed when the damping adjustment blade 801 rotates, generating a dual effect of strong turbulence and throttling damping, adding an additional damping unloading path, forming an adaptive damping force that matches the vibration amplitude in real time, quickly consuming vibration energy and suppressing vibration amplitude. Especially when the motor 9 starts and stops through the resonance zone, it can instantly establish a strong damping force to suppress the resonance peak and prevent the vibration impact from being transmitted to the upper test bearing plate 1.

[0037] Throughout the vibration transmission and damping unloading process, the ball joint seat 701 at the upper end of the ball screw shaft 7 and the spherical groove 102 of the upper test bearing plate 1 form an adaptive spherical hinge fit. With a 1.5mm self-aligning clearance, it compensates in real time for the motor 9's clamping off-center load, installation coaxiality error, and radial runout generated during vibration. The 1.5mm thick rubber layer 103 inside the mounting hole 101 and the hollow rubber sleeve 302 inside the guide sliding hole 301 form a double-end radial vibration isolation and double self-aligning protection system, isolating radial vibration interference and preventing the ball screw shaft 7 from bending or jamming due to additional radial loads. This ensures pure and linear transmission of axial vibration displacement. The 0.2mm thick wear-resistant PTFE coating on the ball joint mating surface significantly reduces sliding friction resistance, ensuring smooth and jam-free self-aligning action, while also extending the mating surface... To ensure durability, a 1.5mm media flow adjustment gap 603 between the damping adjustment blade 801 and the damping medium cavity 602 is established. This gap prevents motion interference between the damping adjustment blade 801 and the cavity wall, while also controlling the shear layer thickness of the viscous damping fluid to form a stable linear shear damping force. The bidirectional sealing ring 604 at the opening of the adjustment sleeve 6 completely seals the damping fluid leakage channel, preventing damping fluid loss and damping force attenuation. The damping unit heat dissipation fins 605 distributed circumferentially on the outer surface of the adjustment sleeve 6, together with the damping adjustment blade 801 and the media flow adjustment hole 802, drive the forced convection of the damping fluid, quickly dissipating the working heat generated by the shearing and turbulence of the damping adjustment blade 801 outward, suppressing the viscosity decrease and damping force attenuation caused by the temperature rise of the damping fluid, and ensuring a stable linear output of damping force during continuous batch testing.

[0038] Ultimately, through the nonlinear adaptive stiffness adjustment of the mirror-mounted conical spring, the axial and then rotational motion conversion from the non-self-locking ball screw shaft 7 to the rotary damping adjustment flywheel 8, the turbulent throttling dual damping and force relief of the damping adjustment blade 801 with medium flow adjustment hole 802, and the multi-dimensional collaborative design of ball joint self-alignment, radial vibration isolation, efficient heat dissipation and sealing protection, active suppression of resonance in a wide frequency range is achieved. At the same time, it can accurately and stably transmit the real vibration signal of the motor 9, ensuring the authenticity and accuracy of the test data collected by the vibration intelligent sensor 2. At the same time, it greatly improves the adaptability of the test platform to working conditions, continuous working capability and long-term operational reliability, and can meet the vibration test requirements of mining motors with different power and different excitation frequencies.

[0039] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the scope of protection of the present invention.

Claims

1. An elastic support platform for whole-machine vibration testing of a mining electric motor, comprising an upper test bearing plate (1), wherein a vibration intelligent sensor (2) is provided on one side of the upper test bearing plate (1), and a test platform base (3) is provided on the lower side of the upper test bearing plate (1), characterized in that, A positive conical spring (4) and a negative conical spring (5) are mirror-arranged between the upper test bearing plate (1) and the test platform base (3). The positive conical spring (4) is supported on the upper test bearing plate (1), and the negative conical spring (5) is supported on the test platform base (3). An adjusting sleeve (6) is provided between the positive conical spring (4) and the negative conical spring (5). The adjusting sleeve (6) has positioning countersunk holes (601) at both ends of its axial direction. The small diameter ends of the positive conical spring (4) and the negative conical spring (5) are respectively covered in the positioning countersunk holes (601). The adjusting sleeve (6) contains... A test vibration damping adjustment unit is provided. The upper test bearing plate (1) has a mounting hole (101) on its lower side. A ball screw shaft (7) is provided in the mounting hole (101). The ball screw shaft (7) is non-self-locking. The ball screw shaft (7) passes through the adjustment sleeve (6) along the axis of the positive conical spring (4). The ball screw shaft (7) drives the test vibration damping adjustment unit to unload the force. The test platform base (3) is provided with a guide sliding hole (301) that is consistent with the position of the ball screw shaft (7). The guide sliding hole (301) slides with the ball screw shaft (7).

2. The elastic support platform for whole-machine vibration testing of a mining electric motor according to claim 1, characterized in that, The test vibration damping adjustment unit includes a damping medium cavity (602) and a rotating damping adjustment flywheel (8). The damping medium cavity (602) is provided inside the adjustment sleeve (6). The damping medium cavity (602) is filled with viscous damping fluid. The rotating damping adjustment flywheel (8) is rotatably arranged inside the damping medium cavity (602) and is completely immersed in the viscous damping fluid. The rotating damping adjustment flywheel (8) and the ball screw shaft (7) are connected by a helical transmission through balls. The outer circumference of the rotating damping adjustment flywheel (8) is provided with damping adjustment blades (801). The ball screw shaft (7) drives the rotating damping adjustment flywheel (8) to rotate inside the damping medium cavity (602) with the vertical displacement of the upper test bearing plate (1).

3. The elastic support platform for whole-machine vibration testing of a mining electric motor according to claim 2, characterized in that, Each of the damping adjustment blades (801) is provided with a medium flow adjustment hole (802), and the medium flow adjustment hole (802) penetrates the damping adjustment blade (801).

4. The elastic support platform for whole-machine vibration testing of a mining electric motor according to claim 2, characterized in that, A medium flow adjustment gap (603) is provided between the damping adjustment blade (801) and the damping medium cavity (602), and the medium flow adjustment gap (603) is 1.5mm to 2mm.

5. The elastic support platform for whole-machine vibration testing of a mining electric motor according to claim 1, characterized in that, The upper end of the ball screw shaft (7) is provided with a ball joint seat (701), and a spherical groove (102) is provided in the mounting hole (101). The ball joint seat (701) is installed in the spherical groove (102). The spherical groove (102) and the ball joint seat (701) are spaced 1mm to 1.5mm apart. When the positive conical spring (4) is not compressed, the spherical groove (102) and the ball joint seat (701) maintain surface contact.

6. The elastic support platform for whole-machine vibration testing of a mining electric motor according to claim 5, characterized in that, A rubber layer (103) is provided between the mounting hole (101) and the ball screw shaft (7), the thickness of the rubber layer (103) is 1mm to 1.5mm, and a hollow cylindrical rubber sleeve (302) is provided between the hole wall of the guide slide hole (301) and the ball screw shaft (7).

7. The elastic support platform for whole-machine vibration testing of a mining electric motor according to claim 1, characterized in that, The openings of the adjusting sleeve (6) through which the ball screw shaft (7) passes are all provided with sealing rings (604).

8. The elastic support platform for whole-machine vibration testing of a mining electric motor according to claim 4, characterized in that, The outer surface of the adjusting sleeve (6) is provided with multiple circumferentially distributed damping unit heat dissipation fins (605).

9. The elastic support platform for whole-machine vibration testing of a mining electric motor according to claim 5, characterized in that, The outer spherical surface (702) of the ball joint seat (701) and the inner spherical surface (104) of the spherical groove (102) are both provided with a wear-resistant polytetrafluoroethylene coating, and the thickness of the coating is 0.2mm to 0.5mm.

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