CN103868691A - Angular contact ball bearing dynamic parameter tester - Google Patents

Abstract

The invention relates to an experimental device for testing dynamic parameters of an angular contact ball bearing, comprising: a leveling pad iron, an experimental platform, a T-shaped base plate, a displacement gauge IPN type damping plate, a displacement gauge bracket, a positioning cylindrical pin, a guide flat key, and a motor IPN Type damping plate, DC motor, TS-B type elastic coupling, vibration exciter bracket, vibration exciter, impedance head, axial loading mechanism, bearing assembly, acceleration sensor, optical pen, CHB type digital display, 24V DC Power supply, CCS type controller, computer with CCSManager software installed, signal conditioner, data collector, computer with CRAS software installed, power amplifier and motor speed controller. Compared with the prior art, the present invention has the remarkable advantages of simple device structure, high positioning accuracy and testing accuracy, and can test the dynamic parameters of bearings under different rotating speeds and axial load conditions; it has strong versatility and can test different Dynamic parameters of the dimension series bearings.

Description

Angular contact ball bearing dynamic parameter testing device

technical field

The invention relates to an experimental device for testing dynamic parameters, in particular to a testing device for dynamic parameters of angular contact ball bearings.

Background technique

With the development of high-end CNC machine tools in the direction of high precision, high speed and high efficiency, as the key functional components in the machine tool, the spindle and feed system must have good dynamic characteristics. Angular contact ball bearings are commonly used rotating support components for machine tool spindles and feed systems, and their dynamic parameters have an important impact on the characteristics of machine tool spindles and feed systems and the characteristics of the whole machine.

At present, in terms of experimental analysis of dynamic parameters of angular contact ball bearings, many researchers have carried out multi-faceted and multi-level research, but most of them stay in the study of the influence of different types and sizes of load conditions on bearing dynamic parameters, and have not yet considered Influence of bearing speed. In practical applications, the speed is a working condition that cannot be ignored for bearings, so the experimental analysis of the influence of different speeds and load conditions on the dynamic parameters of angular contact ball bearings has important research value.

Document 1: Chinese patent: bearing dynamic characteristic parameter testing device, patent application number: 201310024031.6. A test device for dynamic characteristic parameters of bearings based on a single-degree-of-freedom vibration system is designed. The device has a compact structure and a clear test principle, and can test dynamic characteristic parameters of bearings under different axial force, radial force and preload load conditions. However, this device cannot test the dynamic parameters of the bearing under working conditions such as different speeds.

Document 2: Chinese patent: testing device for dynamic and static characteristic parameters of angular contact ball bearings, patent number: 201310281081.2. A testing device for dynamic and static characteristic parameters of angular contact ball bearings, which can test both axial and radial dynamic and static parameters, is designed. The device has simple structure, high testing accuracy and strong versatility. However, this device cannot test the dynamic parameters of the bearing under working conditions such as different speeds.

It can be seen from the above that there is currently no experimental device to test the dynamic parameters of angular contact ball bearings under different rotational speeds and axial load conditions.

Contents of the invention

The technical problem solved by the present invention is to provide a device with simple structure, correct test principle, high positioning accuracy and test accuracy, strong versatility, and can test the axial and radial dynamic parameters of bearings under different speeds and axial loads, etc. Characteristics of the experimental device for testing dynamic parameters of angular contact ball bearings.

The technical solution to realize the object of the present invention is: a dynamic parameter testing experimental device for angular contact ball bearings, including leveling shims, an experimental platform, a T-shaped base plate, a displacement gauge IPN type damping plate, a displacement gauge bracket, a bearing seat, a positioning Cylindrical pin, guide flat key, motor IPN damping plate, DC motor, TS-B elastic coupling, exciter bracket, exciter, impedance head, axial loading mechanism, bearing assembly, acceleration sensor, optical pen , CHB type digital display instrument, 24V DC power supply, CCS type controller, computer with CCS Manager software installed, signal conditioner, data collector, computer with CRAS software installed, power amplifier and motor governor; among them, a displacement meter The bracket includes the lower backing plate of the displacement meter, the lower slider of the displacement meter, the lower feeding bracket of the displacement meter, the lower feeding screw of the displacement meter, the upper backing plate of the displacement meter, the upper slider of the displacement meter, the optical pen holding ring, and the upper feeding bracket of the displacement meter , the upper feed screw of the displacement meter, the lower feed spring of the displacement meter and the upper feed spring of the displacement meter; wherein, a bearing seat includes a lower bearing seat and an upper bearing seat; wherein, the axial loading mechanism includes an elastic ring, an elastic ring backing plate, a right Rotary screw, loading nut, loading rod, left-handed screw, force sensor backing plate and force sensor; wherein, the bearing assembly includes a lock nut, a rotating shaft, a bearing and a bearing sleeve;

The experimental platform is placed on the leveling pad iron, and the T-shaped base plate is fixed on the experimental platform; the bearing seat, displacement gauge bracket and DC motor are arranged on the T-shaped base plate. The number of the bearing seats is two, and one of the bearing seats is close to the DC motor. For the motor, the lower bearing seat of each bearing seat is fixed on the T-shaped base plate by anti-rotation bolts, and a guide flat key and four positioning cylindrical pins are arranged between the lower bearing seat and the T-shaped base plate, and the four positioning cylindrical pins pass through The interference fit is evenly distributed on the four corners of the lower bearing seat. The guide flat key is fixed in the keyway of the T-shaped base plate through the hexagon socket head screw. The guide flat key is located in the middle of the bottom surface of the lower bearing seat. , and positioning cylindrical pins respectively improve the axial movement accuracy and reduce the torsional error in the upper surface of the T-shaped base plate; the upper bearing seat is fixedly connected to the lower bearing seat, and two positioning pins are set between the upper bearing seat and the lower bearing seat , the two positioning pins are fixed on the opposite corners of the upper bearing seat through interference fit;

Two identical displacement gauge brackets are arranged in parallel on the T-shaped base plate, and the two displacement gauge brackets are located between the two bearing seats, and the lower backing plate of the displacement gauge of each displacement gauge bracket is fixed on the T-shaped base plate by hexagon socket screws , the displacement gauge IPN type damping plate is set between the displacement gauge lower backing plate and the T-shaped base plate, the displacement gauge lower slider is located above the displacement gauge lower backing plate, and the displacement is set between the displacement gauge lower backing plate and the displacement gauge lower slider The lower feed spring of the displacement meter. The extension direction of the lower feed spring of the displacement meter is consistent with the feeding direction of the lower feed screw of the displacement meter. The lower feed screw is threaded into the lower feed bracket of the displacement gauge and is perpendicular to the side of the lower feed bracket. The concave spherical surface at one end of the lower feed screw of the displacement gauge is on the convex spherical surface on the side of the lower backing plate of the displacement gauge. , the upper backing plate of the displacement meter is fixed on the lower slider of the displacement meter through the inner hexagonal screw, the upper slider of the displacement meter is located above the upper backing plate of the displacement meter, and the displacement meter is set between the upper backing plate of the displacement meter and the upper slider of the displacement meter The upper feed spring, the extension direction of the upper feed spring of the displacement meter is consistent with the feeding direction of the upper feed screw of the displacement meter. Connected in the upper feeding bracket of the displacement meter and perpendicular to the side of the upper feeding bracket of the displacement meter, the upper feeding screw of the displacement meter is perpendicular to the lower feeding screw of the displacement meter, and the concave spherical surface at one end of the upper feeding screw of the displacement meter is on the displacement On the convex spherical surface on the side of the upper backing plate of the gauge, the optical pen holding ring is fixed on the upper slider of the displacement gauge through cross screws;

The DC motor is fixed on the T-shaped base plate through ordinary hexagonal screws, and the motor IPN type damping plate is set between the DC motor and the T-shaped base plate. The input end of the DC motor is connected to the output end of the motor governor, and the output shaft of the DC motor is passed through Fixed with one end of TS-B elastic coupling;

The bearing assembly is located between the upper bearing seat and the lower bearing seat. The bearing sleeve in the bearing assembly is fixed on the upper bearing seat and the lower bearing seat by ordinary hexagonal screws and positioning pins. The outer ring of the bearing is fixed on the bearing seat by interference fit. In the sleeve, the inner ring is fixed on the shaft through interference fit, and the lock nut is connected to the shaft through threads. The lock nut is pressed against the inner ring of the bearing. The other end is fixed; the rotating shaft is located between the two bearing seats;

Four identical and parallel axial loading mechanisms are arranged between the inner end faces of the two bearing sleeves. The four axial loading mechanisms all adopt the form of twin-screws with different screw directions. On the screw, the elastic ring is cushioned on one end of the elastic ring backing plate and set on the right-handed screw. The polished rod end of the right-handed screw is inserted into the small hole on the inner end surface of the bearing sleeve, so that the elastic ring is close to the inner end surface of the bearing sleeve. The other end of the right-handed screw is connected to one end of the loading nut through the right-handed thread, the loading rod is inserted into the small hole around the loading nut, one end of the left-handed screw is connected to the other end of the loading nut through the left-handed thread, and the other end of the left-handed screw is passed through The gap fit is set in the force sensor backing plate, the end face of the force sensor is fixed on the force sensor backing plate by cross screws, the convex spherical surface of the other end of the force sensor is in the concave groove of the inner end face of the bearing sleeve, the output end of the force sensor is connected with the The input terminal of the CHB digital display instrument is connected;

The optical pen is fixed in the optical pen holding ring, the axis of the optical pen is parallel to the upper surface of the experimental platform, the end face of the optical pen is 15-20mm away from the surface of the side convex ring of the rotating shaft, the output end of the optical pen is connected to the input end of the CCS type controller connected, the output end of the CCS type controller is connected with the 24V DC power supply, and the CCS type controller is connected with the first computer;

The vibration exciter bracket is located above the side of the experimental platform. The vibration exciter bracket is connected to the vibration exciter through an elastic rope. The front end of the vibration exciter is connected to the impedance head through a transmission rod. The axis of the impedance head is parallel to the upper plane of the experimental platform. The end face of the impedance head is 5±1.5mm away from the surface of the middle convex ring of the rotating shaft. The acceleration sensor is placed on the horizontal radial groove surface of the bearing sleeve through a magnetic suction cup. The force signal output end of the impedance head and the output end of the acceleration sensor are connected with the signal conditioner. The output end of the signal conditioner is connected to the input end of the data collector, the A-type USB interface of the data collector is connected to the computer installed with CRAS software through the data cable, the output end of the data collector is connected to the input end of the power amplifier, and the power The output of the amplifier is connected to the input of the exciter.

The spherical top cylinder on the inner end surface of the lower slider of the displacement meter is matched with the U-shaped groove on the outer end surface of the lower backing plate of the displacement meter. The gap between the lower surface of the lower slider of the displacement meter and the upper surface of the lower backing plate of the displacement meter is 0.5~ 1mm; the spherical top cylinder on the inner end surface of the upper slider of the displacement gauge matches the U-shaped groove on the outer end surface of the lower backing plate of the displacement meter, and the gap between the lower surface of the lower slider of the displacement meter and the upper surface of the lower backing plate of the displacement meter is 0.5～1mm.

The guide flat key and the side of the keyway at the bottom of the lower bearing seat are clearance fit, and the fit type is F6/h5.

The roughness of the upper surface of the experimental platform where the displacement meter IPN type damping plate and the motor IPN type damping plate are installed and the lower surface of the displacement meter lower backing plate is within the range of 0.63-1.25 μm.

The number of acceleration sensors is four, and the number of optical pens is two.

It also includes leveling pads, the number of leveling pads is four, and the four leveling pads are respectively arranged on the four corners below the experimental platform.

Compared with the prior art, the present invention has the following significant advantages: (1) In the displacement meter bracket, the threaded parts of the upper feed screw of the displacement meter and the lower feed screw of the displacement meter have the characteristics of multi-thread, small pitch, fine teeth, etc. The position of the optical pen in the horizontal plane can be fine-tuned by moving different feed screws, so the structure of the displacement gauge bracket is simple, the operation is convenient, and the positioning accuracy is high; (2) The displacement gauge bracket is equipped with a displacement gauge upper feed spring and a lower feed spring. The spring can well weaken the crawling phenomenon when adjusting the position of the optical pen; (3) Adopt four axial loading mechanisms, which can improve the loading accuracy and increase the maximum bearing test load; (4) The distance between the displacement meter bracket and the experimental platform The IPN damping plate of the displacement meter is installed between them, which can greatly reduce the influence of the vibration of the DC motor and the exciter on the position of the optical pen, and improve the accuracy of the test results; (5) The IPN damping plate of the motor is set between the DC motor and the experimental platform , can well reduce the impact of DC motor vibration on other mechanical structures on the experimental platform; (6) TS-B elastic coupling is used between the DC motor and the rotating shaft, which can greatly reduce the unbalanced vibration of the DC motor output shaft The impact on the rotating shaft; (7) Angular contact ball bearings of other sizes can be tested only by replacing different bearing sleeves and rotating shafts, which improves the versatility of the experiment and reduces the cost of experimental research.

Description of drawings

Fig. 1 is an overall structural diagram of an experimental device for testing dynamic parameters of an angular contact ball bearing of the present invention.

Figure 2 is a structural diagram of the displacement meter support in the experimental device for testing the dynamic parameters of angular contact ball bearings of the present invention, Figure (a) is a three-dimensional axonometric view, Figure (b) is a main sectional view, and Figure (c) is a side sectional view.

Fig. 3 is a structural diagram of a bearing housing in an experimental device for testing dynamic parameters of an angular contact ball bearing according to the present invention.

Fig. 4 is a structural diagram of the axial loading mechanism in the experimental device for testing the dynamic parameters of the angular contact ball bearing of the present invention.

Fig. 5 is a structural diagram of the bearing assembly in the experimental device for testing the dynamic parameters of the angular contact ball bearing of the present invention: Fig. (a) is a three-dimensional isometric view, and Fig. (b) is a main sectional view.

Fig. 6 is a mechanical model for testing the radial dynamic parameters of the bearing assembly of the present invention.

Fig. 7 is a mechanical model for testing the axial dynamic parameters of the bearing assembly of the present invention.

Fig. 8 is a wireframe diagram of the dynamic displacement test system of Shanghai Sixin Dispersion Confocal Displacement Meter CCS Manager according to the present invention.

Fig. 9 is a wireframe diagram of the Nanjing Anzheng CRAS modal analysis testing system of the present invention.

Detailed ways

With reference to Fig. 1, Fig. 2, Fig. 3, Fig. 4 and Fig. 5, the present invention discloses an experimental device for testing dynamic parameters of angular contact ball bearings, which is used to test angular contact within the range of inner diameter Φ30-Φ60 and outer diameter Φ55-Φ110. Dynamic parameters of ball bearings at different speeds and axial loads. The device includes leveling pad iron 1, experimental platform 2, T-shaped base plate 3, displacement gauge IPN damping plate 4, displacement gauge bracket 5, bearing seat 6, positioning cylindrical pin 7, guide flat key 8, motor IPN damping plate 9. DC motor 10, TS-B type elastic coupling 11, exciter bracket 12, exciter 13, impedance head 14, axial loading mechanism 15, bearing assembly 16, acceleration sensor 17, optical pen 18, CHB Type digital display instrument 19, 24V DC power supply 20, CCS type controller 21, first computer 22, signal conditioner 23, data collector 24, second computer 25, power amplifier 26, motor governor 27; The quantity of meter support is two, and each displacement meter support 5 all comprises displacement meter lower backing plate 5a, displacement meter lower slider 5b, displacement meter lower feed support 5c, displacement meter lower feed screw rod 5d, displacement meter upper pad Plate 5e, displacement gauge upper slider 5f, optical pen holding ring 5g, displacement gauge upper feed bracket 5h, displacement gauge upper feed screw 5i, displacement gauge lower feed spring 5j and displacement gauge upper feed spring 5k; The number is two, and each bearing seat 6 includes a lower bearing seat 6a and an upper bearing seat 6b; wherein, the axial loading mechanism 15 includes an elastic ring 15a, an elastic ring backing plate 15b, a right-handed screw 15c, a loading nut 15d, a loading Rod 15e, left-hand screw 15f, force sensor backing plate 15g and force sensor 15h; wherein, the bearing assembly 16 includes a lock nut 16a, a rotating shaft 16b, a bearing 16c and a bearing sleeve 16d;

The experimental platform 2 is placed on the leveling pad iron 1, and the T-shaped base plate 3 is fixed on the experimental platform 2; the T-shaped base plate 3 is provided with a bearing seat 6, a displacement meter bracket 5 and a DC motor 10, and the number of the bearing seats is two One of the bearing seats is close to the DC motor, and the lower bearing seat 6a of each bearing seat 6 is fixed on the T-shaped base plate 3 by anti-rotation bolts, and a guide flat key 8 is set between the lower bearing seat 6a and the T-shaped base plate 3 And four positioning cylindrical pins 7, the four positioning cylindrical pins 7 are evenly fixed on the four corners of the lower bearing seat 6a through interference fit, and the guide flat key 8 is fixed in the keyway of the T-shaped base plate 3 by hexagon socket head screws. Located in the middle of the bottom surface of the lower bearing seat 6a, the bearing seat 6 improves its axial movement accuracy and reduces the torsional error on the upper surface of the T-shaped base plate 3 through the guide flat key 8 and the positioning cylindrical pin 7 respectively; the upper bearing seat 6b is fixedly connected On the lower bearing seat 6a, two positioning pins are arranged between the upper bearing seat 6b and the lower bearing seat 6a, and the two positioning pins are fixed on the opposite corners of the upper bearing seat 6b through interference fit;

Two identical displacement gauge brackets 5 are arranged in parallel on the T-shaped base plate, and the two displacement gauge brackets 5 are located between two bearing seats 6. The displacement gauge lower backing plate 5a of each displacement gauge bracket 5 is fixed on On the T-shaped base plate 3, the displacement gauge IPN type damping plate 4 is arranged between the displacement gauge lower backing plate 5a and the T-shaped base plate 3, the displacement gauge lower slider 5b is located above the displacement gauge lower backing plate 5a, and the displacement gauge lower backing plate Displacement gauge lower feed spring 5j is set between displacement gauge lower slider 5a and displacement gauge lower slider 5b, displacement gauge lower feed bracket 5c is fixed on the side of displacement gauge lower slider 5b by hexagon socket head screws, and displacement gauge lower feed screw 5d passes thread Connected in the lower feed bracket 5c of the displacement meter, the concave spherical surface on the side of the lower feed screw 5d of the displacement meter is on the convex spherical surface on the side of the lower backing plate 5a of the displacement meter, and the upper backing plate 5e of the displacement meter is fixed by hexagon socket screws On the displacement gauge lower slider 5b, the displacement gauge upper slider 5f is located above the displacement gauge upper backing plate 5e, and the displacement gauge upper feed spring 5k is set between the displacement gauge upper backing plate 5e and the displacement gauge upper slider 5f, and the displacement The upper feed bracket 5h of the displacement gauge is fixed on the side of the upper slider 5f of the displacement gauge through the inner hexagonal screw. The convex spherical surface on the side of the backing plate 5e on the displacement meter, the optical pen holding ring 5g is fixed on the upper slider 5f of the displacement meter through cross screws;

The DC motor 10 is fixed on the T-shaped base plate 3 by common hexagonal screws, a motor IPN type damping plate 9 is arranged between the DC motor 10 and the T-shaped base plate 3, and the input end of the DC motor 10 is connected to the output end of the motor governor 27. The output shaft of the DC motor 11 is fixed to one end of the TS-B elastic coupling 11 through a pin;

The bearing assembly 16 is located between the upper bearing seat 6b and the lower bearing seat 6a, and the bearing sleeve 16d in the bearing assembly 16 is fixed on the upper bearing seat 6b and the lower bearing seat 6a by common hexagon screws and positioning pins, and the outer surface of the bearing 16c The ring is fixed in the bearing sleeve 16d through interference fit, the inner ring is fixed on the rotating shaft 16b through interference fit, and the lock nut 16a is connected to the rotating shaft 16b through threads. The lock nut 16a is pressed against the inner ring of the bearing 16c, and the rotating shaft One end of 16b is fixed with the other end of TS-B elastic coupling 11 through a pin;

An axial loading mechanism 15 is arranged between the inner end faces of the bearing sleeve 16d. The axial loading mechanism 15 adopts the form of twin screws with different screw directions. The elastic ring backing plate 15b is sleeved on the right-handed screw 15c through clearance fit, and the elastic ring 15a Pad one end of the elastic ring backing plate 15b and cover it on the right-handed screw 15c, one end of the polished rod of the right-handed screw 15c is inserted into the small hole in the inner end surface of the bearing sleeve 16d, so that the elastic ring 14a is close to the inner end surface of the bearing sleeve 16d, The other end of the right-handed screw 14c is connected to one end of the loading nut 15d by a right-handed thread, the loading rod 15e is inserted in the small hole around the loading nut 15d, and one end of the left-handed screw 15f is connected to the other end of the loading nut 15d by a left-handed thread. The other end of the left-handed screw 15f is sleeved in the force sensor backing plate 15g through a clearance fit, the end face of the force sensor 15h is fixed on the force sensor backing plate 15g by cross screws, and the convex spherical surface of the other end of the force sensor 15h is pushed against the bearing sleeve 16d In the concave groove of the end face, the output end of the force sensor 15h is connected with the input end of the CHB digital display instrument 19;

The optical pen 18 is fixed in the optical pen holding ring 5g, the axis of the optical pen 18 is parallel to the upper surface of the experimental platform 2, the end face of the optical pen 18 is 15-20mm from the side convex ring surface of the rotating shaft 16b, the output end of the optical pen 18 is connected to the The input end of the CCS type controller 21 is connected, the output end of the CCS type controller 21 is connected with the 24V DC power supply 20, and the CCS type controller 21 is connected with the first computer 22;

The vibrator bracket 12 is located above the side of the experimental platform 2. The vibrator bracket 12 is connected to the vibrator 13 through an elastic rope. The front end of the vibrator 13 is connected to the impedance head 14 through a transfer rod, and the axis of the impedance head 14 is parallel to the On the upper plane of the experimental platform 2, the end face of the impedance head 14 is 5 ± 1.5mm from the middle convex ring surface of the rotating shaft 16b, the acceleration sensor 17 is placed on the horizontal radial groove surface of the bearing sleeve 16d through a magnetic chuck, and the force of the impedance head 14 The signal output terminal and the output terminal of the acceleration sensor 17 are connected with the signal conditioning instrument 23, and the output terminal of the signal conditioning instrument 23 is connected with the input terminal of the data collector 24, and the data collector 24 is connected with the second computer 25, and the data collector 24 The output terminal is connected to the input terminal of the power amplifier 26 , and the output terminal of the power amplifier 26 is connected to the input terminal of the exciter 13 .

Wherein the first computer 22 is equipped with CCS Manager software, and the second computer 25 is equipped with CRAS software.

The spherical top surface cylinder of the inner end surface of the lower slider 5b of the displacement meter is matched with the U-shaped groove on the outer end surface of the lower backing plate 5a of the displacement meter, and the lower surface of the lower slider 5b of the displacement meter and the upper surface of the lower backing plate 5a of the displacement meter The gap between them is in the range of 0.5 ~ 1mm; the spherical top cylinder on the inner end surface of the upper slider 5f of the displacement meter is matched with the U-shaped groove on the outer end surface of the lower backing plate 5e of the displacement meter, and the lower surface of the lower slider 5f of the displacement meter is in line with the displacement The gap between the upper surfaces of the lower backing plates 5e is calculated to be in the range of 0.5-1mm.

The guide flat key 8 and the side of the keyway at the bottom of the lower bearing seat 6a are clearance fit, and the fit type is F6/h5.

The roughness of the upper surface of the experimental platform 2 on which the displacement meter IPN type damping plate 4 and the motor IPN type damping plate 9 are installed and the lower surface of the displacement meter lower backing plate 5a is within the range of 0.63-1.25 μm.

The number of acceleration sensors 17 is four, and the number of optical pens 18 is two.

The experimental device of the present invention also includes leveling pads 1 , the number of which is four, and the four leveling pads 1 are respectively arranged on four corners below the experimental platform 2 .

Specifically, the experimental platform 2 is placed on four leveling pad irons 1. Before the experiment, the T-shaped base plate 3 should be leveled to improve the installation accuracy of the vibrator 13 and the optical pen 18; One M20 ordinary hexagonal screw is fixed on the experimental platform 2. Before the experiment, all the connecting screws should be tightened to improve the modal parameters of the fixed joint surface and reduce the influence on the modal parameters of the bearing joint surface; the displacement meter bracket 5 passes through six M6 inner hexagon screws and displacement gauge IPN damping plate 4 are fixed on the experimental platform 2. Before the experiment, all screws should be tightened to reduce the influence of the vibration of the basic components on the position of the optical pen during the experiment; the DC motor 10 passes through six M14 ordinary The hexagonal screws are fixed on the experimental platform 2 to reduce the unbalanced vibration of the DC motor 10, reduce the impact on the vibration response of the rotating shaft, and improve the test accuracy; the output shaft of the DC motor 10 is connected to the rotating shaft through a Φ8 pin to ensure the transmission of rotational motion rate of 100%; four axial loading mechanisms 15 are used to improve loading accuracy and increase the maximum bearing test load; the applied axial load can be read directly from the CHB digital display 19, and the bearing speed can be directly read from the motor Read it on the display panel of the governor 27; when the axial load is loaded and the bearing rotation is stable, open the computer 22 and the computer 25 with the CCSManager software installed and the CRAS software installed respectively, run the CCS Manager software and the CRAS software, and open the mold The dynamic test excitation system and the dynamic micro-displacement test system simultaneously pick up the force signal of the impedance head 14, the vibration displacement signal of the test point of the rotating shaft 16b and the vibration acceleration signal of the test point of the bearing sleeve 16d.

Combining Fig. 1, Fig. 6 and Fig. 7, the basic principle of the testing experimental device for dynamic parameter testing of angular contact ball bearings is to take the bearing assembly 16 as the research object, and establish a single-degree-of-freedom dynamic parameter testing mechanics that eliminates the vibration response of the foundation (bearing sleeve 16d). A model that identifies the axial and radial dynamic stiffness and damping of the bearing. In the process of testing and identification of this device, the rotating shaft 16b with a sufficiently large structural size is regarded as the mass block M, the bearing sleeve 16d fixedly constrained in the bearing seat 6 is regarded as the basic mass block M ₀ , and all the balls in the bearing 16c The dynamic contact characteristic of is equivalent to an array of spring damping units. According to the parallel nature of the spring, the equivalent model can be simplified into a radial and axial single-degree-of-freedom vibration system; the displacement signal of the test point on the rotating shaft 16b is used as a mass For the vibration response, the acceleration signal of the test point on the bearing sleeve 16d is used as the basic vibration response.

Assuming that the exciting force signal is f(t), the vibration response signal of the mass block is x _M (t), and the vibration response signal of the basic mass block is a _B (t), firstly, the least square method is used to fit the obtained test data x(t ), and then derive the corresponding acceleration data a _M (t), and finally use the self-written LEVY method modal parameter identification program to obtain the radial and axial dynamic stiffness and damping of the bearing.

Combined with Fig. 6, when the mass M is subjected to the radial simple harmonic excitation force f(t), its vibration differential equation can be expressed as

${\mathrm{<span\; class="notranslate">\; m</span>}\stackrel{<span\; class="notranslate">\; \&Center\; Dot;</span><span\; class="notranslate">\; \&Center\; Dot;</span>}{\mathrm{<span\; class="notranslate">\; x</span>}}}_{\mathrm{<span\; class="notranslate">\; m</span>}}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; t</span>}<span\; class="notranslate">\; )</span><span\; class="notranslate">\; +</span>{\mathrm{<span\; class="notranslate">\; C</span>}}_{\mathrm{<span\; class="notranslate">\; R</span>}}<span\; class="notranslate">\; (</span>{\stackrel{<span\; class="notranslate">\; \&CenterDot;</span>}{\mathrm{<span\; class="notranslate">\; x</span>}}}_{\mathrm{<span\; class="notranslate">\; m</span>}}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; t</span>}<span\; class="notranslate">\; )</span><span\; class="notranslate">\; -</span>{\stackrel{<span\; class="notranslate">\; \&Center\; Dot;</span>}{\mathrm{<span\; class="notranslate">\; x</span>}}}_{\mathrm{<span\; class="notranslate">\; B</span>}}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; t</span>}<span\; class="notranslate">\; )</span><span\; class="notranslate">\; )</span><span\; class="notranslate">\; +</span>{\mathrm{<span\; class="notranslate">\; K</span>}}_{\mathrm{<span\; class="notranslate">\; R</span>}}<span\; class="notranslate">\; (</span>{\mathrm{<span\; class="notranslate">\; x</span>}}_{\mathrm{<span\; class="notranslate">\; m</span>}}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; t</span>}<span\; class="notranslate">\; )</span><span\; class="notranslate">\; -</span>{\mathrm{<span\; class="notranslate">\; x</span>}}_{\mathrm{<span\; class="notranslate">\; B</span>}}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; t</span>}<span\; class="notranslate">\; )</span><span\; class="notranslate">\; )</span><span\; class="notranslate">\; =</span>\mathrm{<span\; class="notranslate">\; f</span>}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; t</span>}<span\; class="notranslate">\; )</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; 1</span>}<span\; class="notranslate">\; )</span>$

In the formula: M is the sum of the mass of the rotating shaft, the inner rings of the two bearings and all the balls of a single bearing, K _R , C _R are the radial dynamic stiffness and damping of the bearing assembly, x _M (t), x _B (t ) are the radial response displacements of the rotating shaft and foundation (bearing sleeve), respectively.

Perform the following Fourier transform on formula (1): x _M (t)=X _M (ω)e ^jωt , x _B (t)=X _B (ω)e ^jωt and f(t)=F(ω)e ^jωt , Simplified, the displacement frequency response function H _dR (ω) of the single-degree-of-freedom vibration system composed of mass M, stiffness K _R , and damping C _R can be obtained as

${\mathrm{<span\; class="notranslate">\; h</span>}}_{\mathrm{<span\; class="notranslate">\; d</span>}}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; \&omega;</span>}<span\; class="notranslate">\; )</span><span\; class="notranslate">\; =</span>\frac{{\mathrm{<span\; class="notranslate">\; h</span>}}_{\mathrm{<span\; class="notranslate">\; x</span>}<span\; class="notranslate">\; -</span>\mathrm{<span\; class="notranslate">\; Y</span>}}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; \&omega;</span>}<span\; class="notranslate">\; )</span>}{\mathrm{<span\; class="notranslate">\; 1</span>}<span\; class="notranslate">\; +</span>{\mathrm{<span\; class="notranslate">\; M\&omega;</span>}}^{\mathrm{<span\; class="notranslate">\; 2</span>}}{\mathrm{<span\; class="notranslate">\; h</span>}}_{\mathrm{<span\; class="notranslate">\; Y</span>}}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; \&omega;</span>}<span\; class="notranslate">\; )</span>}<span\; class="notranslate">\; -</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; 2</span>}<span\; class="notranslate">\; )</span>$

in:

${\mathrm{<span\; class="notranslate">\; h</span>}}_{\mathrm{<span\; class="notranslate">\; x</span>}<span\; class="notranslate">\; -</span>\mathrm{<span\; class="notranslate">\; Y</span>}}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; \&omega;</span>}<span\; class="notranslate">\; )</span><span\; class="notranslate">\; =</span>\frac{\mathrm{<span\; class="notranslate">\; x</span>}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; \&omega;</span>}<span\; class="notranslate">\; )</span><span\; class="notranslate">\; -</span>\mathrm{<span\; class="notranslate">\; Y</span>}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; \&omega;</span>}<span\; class="notranslate">\; )</span>}{\mathrm{<span\; class="notranslate">\; f</span>}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; \&omega;</span>}<span\; class="notranslate">\; )</span>}$

${\mathrm{<span\; class="notranslate">\; h</span>}}_{\mathrm{<span\; class="notranslate">\; Y</span>}}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; \&omega;</span>}<span\; class="notranslate">\; )</span><span\; class="notranslate">\; =</span>\frac{\mathrm{<span\; class="notranslate">\; Y</span>}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; \&omega;</span>}<span\; class="notranslate">\; )</span>}{\mathrm{<span\; class="notranslate">\; f</span>}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; \&omega;</span>}<span\; class="notranslate">\; )</span>}$

In the formula: H _XY (ω) is the vector difference of the frequency response function between the shaft and the foundation; H _Y (ω) is the frequency response function of the foundation displacement.

Therefore, through formula (2), the modal frequency ω _nR and the modal damping ratio ξ _R corresponding to the radial translation mode of the bearing assembly can be identified according to the half power bandwidth method.

Furthermore, the radial dynamic stiffness and damping of a single bearing can be obtained by

${\mathrm{<span\; class="notranslate">\; <figure-callout\; id="0"\; label="K\; R"\; filenames="HDA0000473651140000041.png"\; state="\{\{state\}\}">K</figure-callout></span><figure-callout\; id="0"\; label="K\; R"\; filenames="HDA0000473651140000041.png"\; state="\{\{state\}\}">\; </figure-callout>}}_{\mathrm{<span\; class="notranslate">\; </span>}}<span\; class="notranslate">\; =</span>\mathrm{<span\; class="notranslate">\; 0.5</span>}\mathrm{<span\; class="notranslate">\; m</span>}{\mathrm{<span\; class="notranslate">\; \&omega;</span>}}_{\mathrm{<span\; class="notranslate">\; nR</span>}}^{\mathrm{<span\; class="notranslate">\; 2</span>}}<span\; class="notranslate">\; -</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; 3</span>}<span\; class="notranslate">\; )</span>$

C _R0 = Mω _nR ξ _R (4)

Combined with Fig. 7, when the mass M is subjected to the axial simple harmonic excitation force f(t), its vibration differential equation can be expressed as

$\mathrm{<span\; class="notranslate">\; m</span>}\stackrel{<span\; class="notranslate">\; \&Center\; Dot;</span><span\; class="notranslate">\; \&Center\; Dot;</span>}{\mathrm{<span\; class="notranslate">\; x</span>}}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; t</span>}<span\; class="notranslate">\; )</span><span\; class="notranslate">\; +</span>{\mathrm{<span\; class="notranslate">\; C</span>}}_{\mathrm{<span\; class="notranslate">\; A</span>}}<span\; class="notranslate">\; (</span>{\stackrel{<span\; class="notranslate">\; \&Center\; Dot;</span>}{\mathrm{<span\; class="notranslate">\; x</span>}}}_{\mathrm{<span\; class="notranslate">\; m</span>}}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; t</span>}<span\; class="notranslate">\; )</span><span\; class="notranslate">\; -</span>{\stackrel{<span\; class="notranslate">\; \&Center\; Dot;</span>}{\mathrm{<span\; class="notranslate">\; x</span>}}}_{\mathrm{<span\; class="notranslate">\; B</span>}}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; t</span>}<span\; class="notranslate">\; )</span><span\; class="notranslate">\; )</span><span\; class="notranslate">\; +</span>{\mathrm{<span\; class="notranslate">\; K</span>}}_{\mathrm{<span\; class="notranslate">\; A</span>}}<span\; class="notranslate">\; (</span>{\mathrm{<span\; class="notranslate">\; x</span>}}_{\mathrm{<span\; class="notranslate">\; m</span>}}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; t</span>}<span\; class="notranslate">\; )</span><span\; class="notranslate">\; -</span>{\mathrm{<span\; class="notranslate">\; x</span>}}_{\mathrm{<span\; class="notranslate">\; B</span>}}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; t</span>}<span\; class="notranslate">\; )</span><span\; class="notranslate">\; )</span><span\; class="notranslate">\; =</span>\mathrm{<span\; class="notranslate">\; f</span>}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; t</span>}<span\; class="notranslate">\; )</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; 5</span>}<span\; class="notranslate">\; )</span>$

In the formula: M is the sum of the mass of the rotating shaft, the inner rings of the two bearings and all the balls of a single bearing, K _A and C _A are the axial dynamic stiffness and damping of the bearing assembly respectively, x _M (t), x _B (t ) are the axial response displacements of the rotating shaft and the foundation, respectively.

Perform the following Fourier transform on formula (5): x _M (t)=X _M (ω)e ^jωt , x _B (t)=X _B (ω)e ^jωt and f(t)=F(ω)e ^jωt , Simplified, the displacement frequency response function H _dA (ω) of the single-degree-of-freedom vibration system composed of mass M, stiffness K _A , and damping C _A can be obtained as

${\mathrm{<span\; class="notranslate">\; h</span>}}_{\mathrm{<span\; class="notranslate">\; D</span>}}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; \&omega;</span>}<span\; class="notranslate">\; )</span><span\; class="notranslate">\; =</span>\frac{{\mathrm{<span\; class="notranslate">\; h</span>}}_{\mathrm{<span\; class="notranslate">\; x</span>}<span\; class="notranslate">\; -</span>\mathrm{<span\; class="notranslate">\; Y</span>}}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; \&omega;</span>}<span\; class="notranslate">\; )</span>}{\mathrm{<span\; class="notranslate">\; 1</span>}<span\; class="notranslate">\; +</span>{\mathrm{<span\; class="notranslate">\; M\&omega;</span>}}^{\mathrm{<span\; class="notranslate">\; 2</span>}}{\mathrm{<span\; class="notranslate">\; h</span>}}_{\mathrm{<span\; class="notranslate">\; Y</span>}}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; \&omega;</span>}<span\; class="notranslate">\; )</span>}<span\; class="notranslate">\; -</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; 6</span>}<span\; class="notranslate">\; )</span>$

in:

${\mathrm{<span\; class="notranslate">\; h</span>}}_{\mathrm{<span\; class="notranslate">\; x</span>}<span\; class="notranslate">\; -</span>\mathrm{<span\; class="notranslate">\; Y</span>}}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; \&omega;</span>}<span\; class="notranslate">\; )</span><span\; class="notranslate">\; =</span>\frac{\mathrm{<span\; class="notranslate">\; x</span>}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; \&omega;</span>}<span\; class="notranslate">\; )</span><span\; class="notranslate">\; -</span>\mathrm{<span\; class="notranslate">\; Y</span>}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; \&omega;</span>}<span\; class="notranslate">\; )</span>}{\mathrm{<span\; class="notranslate">\; f</span>}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; \&omega;</span>}<span\; class="notranslate">\; )</span>}$

${\mathrm{<span\; class="notranslate">\; h</span>}}_{\mathrm{<span\; class="notranslate">\; Y</span>}}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; \&omega;</span>}<span\; class="notranslate">\; )</span><span\; class="notranslate">\; =</span>\frac{\mathrm{<span\; class="notranslate">\; Y</span>}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; \&omega;</span>}<span\; class="notranslate">\; )</span>}{\mathrm{<span\; class="notranslate">\; f</span>}<span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; \&omega;</span>}<span\; class="notranslate">\; )</span>}$

In the formula: H _XY (ω) is the vector difference of the frequency response function between the shaft and the foundation; H _Y (ω) is the frequency response function of the foundation displacement.

Therefore, through formula (6), the modal frequency ω _nA and the modal damping ratio ξ _A corresponding to the axial translation vibration mode of the bearing assembly can be identified according to the half power bandwidth method.

Furthermore, the axial dynamic stiffness and damping of a single bearing can be obtained by

${\mathrm{<span\; class="notranslate">\; K</span>}}_{\mathrm{<span\; class="notranslate">\; A</span>}\mathrm{<span\; class="notranslate">\; 0</span>}}<span\; class="notranslate">\; =</span>\mathrm{<span\; class="notranslate">\; 0.5</span>}\mathrm{<span\; class="notranslate">\; m</span>}{\mathrm{<span\; class="notranslate">\; \&omega;</span>}}_{\mathrm{<span\; class="notranslate">\; n</span>}}^{\mathrm{<span\; class="notranslate">\; 2</span>}}<span\; class="notranslate">\; -</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; -</span><span\; class="notranslate">\; (</span>\mathrm{<span\; class="notranslate">\; 7</span>}<span\; class="notranslate">\; )</span>$

C _A0 = Mω _nA ξ _A (8)

It can be seen from the above that the experimental device of the present invention has simple structure, convenient operation, high positioning accuracy and testing accuracy, rigorous and clear testing principle, strong versatility, and can meet the requirements of testing angular contact balls of different size series under different rotational speeds and axial load conditions. Requirements for bearing dynamic parameters.

Claims (6)

1. An angular contact ball bearing dynamic parameter testing experimental device is characterized in that it includes an experimental platform [2], a T-shaped base plate [3], a displacement gauge IPN type damping plate [4], and two identical displacement gauge supports [ 5], bearing seat [6], positioning cylindrical pin [7], guide flat key [8], motor IPN damping plate [9], DC motor [10], TS-B elastic coupling [11], Exciter bracket[12], exciter[13], impedance head[14], axial loading mechanism[15], bearing assembly[16], acceleration sensor[17], optical pen[18], CHB type Display instrument [19], 24V DC power supply [20], CCS type controller [21], first computer [22], signal conditioner [23], data collector [24], second computer [25], power Amplifier [26], motor governor [27]; wherein, each displacement gauge bracket [5] includes displacement gauge lower backing plate [5a], displacement gauge lower slider [5b], displacement gauge lower feed bracket [ 5c], displacement gauge lower feed screw[5d], displacement gauge upper backing plate[5e], displacement gauge upper slider[5f], optical pen retaining ring[5g], displacement gauge upper feed bracket[5h], displacement gauge Upper feed screw [5i], displacement gauge lower feed spring [5j] and displacement gauge upper feed spring [5k]; bearing seat [6] includes lower bearing seat [6a] and upper bearing seat [6b]; axial loading mechanism [15] includes elastic ring [15a], elastic ring backing plate [15b], right-hand screw [15c], loading nut [15d], loading rod [15e], left-hand screw [15f], force sensor backing plate [15g] And force sensor [15h]; Bearing assembly [16] includes lock nut [16a], rotating shaft [16b], bearing [16c] and bearing sleeve [16d]; The T-shaped substrate [3] is fixed on the experimental platform [2], and the T-shaped substrate [3] is provided with a bearing seat [6], a displacement meter support [5] and a DC motor [10], and the bearing seat [6] The number is two, one of the bearing seats is close to the DC motor [10], the lower bearing seat [6a] of each bearing seat [6] is fixed on the T-shaped base plate [3] by anti-rotation bolts, and the lower bearing seat [6a] ] and the T-shaped base plate [3] are provided with a guide flat key [8] and four positioning cylindrical pins [7], and the four positioning cylindrical pins [7] are uniformly fixed on the lower bearing seat [6a] through interference fit On the four corners, the guide flat key [8] is fixed in the keyway of the T-shaped base plate [3] through the hexagon socket head cap screw, and the guide flat key [8] is located in the middle of the bottom surface of the lower bearing seat [6a]. The bearing seat [ 6] Improve the axial movement accuracy and reduce the torsion error in the upper surface of the T-shaped base plate [3] through the guide flat key [8] and the positioning cylindrical pin [7] respectively; the upper bearing seat [6b] is fixedly connected to the lower bearing On the seat [6a], set two positioning pins between the upper bearing seat [6b] and the lower bearing seat [6a], and the two positioning pins are fixed on the opposite corners of the upper bearing seat [6b] through interference fit; Two identical displacement gauge brackets [5] are arranged in parallel on the T-shaped base plate [3]. The plates [5a] are all fixed on the T-shaped base plate [3] by hexagon socket head cap screws, and the displacement gauge IPN type damping plate [4] is set between the displacement gauge lower backing plate [5a] and the T-shaped base plate [3]. The slider [5b] is located above the displacement gauge lower backing plate [5a], and the displacement gauge lower feed spring [5j] is set between the displacement gauge lower backing plate [5a] and the displacement gauge lower slider [5b]. The stretching direction of the lower feed spring [5j] is consistent with the feeding direction of the lower feed screw [5d] of the displacement gauge, and the lower feed bracket [5c] of the displacement gauge is fixed on the lower slider [5b] of the displacement gauge by an inner hexagon screw. On the side, the lower feed screw [5d] of the displacement gauge is connected in the lower feed bracket [5c] of the displacement gauge through threads and is perpendicular to the side of the lower feed bracket [5c]. The concave spherical surface rests on the convex spherical surface on the side of the lower backing plate [5a] of the displacement meter, the upper backing plate [5e] of the displacement meter is fixed on the lower slider [5b] of the displacement meter through the hexagon socket head screw, and the upper slider [5b] of the displacement meter [ 5f] is located above the upper backing plate [5e] of the displacement meter, and the upper feed spring [5k] of the displacement meter is set between the upper backing plate [5e] of the displacement meter and the upper slider [5f] of the displacement meter, and the upper feed spring [5k] of the displacement meter [ The stretching direction of 5k] is consistent with the feeding direction of the upper feed screw [5i] of the displacement meter. The upper feed bracket [5h] of the displacement meter is fixed on the side of the upper slider [5f] of the displacement meter through the inner hexagonal screw, and the upper feed screw of the displacement meter [5i] is threadedly connected in the upper feed bracket [5h] of the displacement meter and is perpendicular to the side of the upper feed bracket [5h] of the displacement meter, and the upper feed screw [5i] of the displacement meter is connected with the lower feed screw [5d of the displacement meter] ] are perpendicular to each other, the concave spherical surface at one end of the feed screw [5i] on the displacement meter is pushed against the convex spherical surface on the side of the backing plate [5e] on the displacement meter, and the optical pen holding ring [5g] is fixed on the displacement meter by cross screws. on block [5f]; The DC motor [10] is fixed on the T-shaped base plate [3] by ordinary hexagonal screws, and the motor IPN type damping plate [9] is set between the DC motor [10] and the T-shaped base plate [3]. The DC motor [10] and the motor The governor [27] is connected, and the output shaft of the DC motor [11] is fixed with one end of the TS-B type elastic coupling [11] by a pin; A bearing assembly [16] is arranged between the upper bearing seat [6b] and the lower bearing seat [6a]. The bearing sleeve [16d] in the bearing assembly [16] is fixed on the upper bearing seat [6b] by ordinary hexagonal screws and positioning pins. ] and the lower bearing seat [6a], the outer ring of the bearing [16c] is fixed in the bearing sleeve [16d] through interference fit, and the inner ring of the bearing [16c] is fixed on the rotating shaft [16b] through interference fit, and the lock The lock nut [16a] is threadedly connected to the rotating shaft [16b]. The lock nut [16a] pushes against the inner ring of the bearing [16c]. One end of the rotating shaft [16b] is connected to the TS-B elastic coupling [ 11] is fixed at the other end; the rotating shaft [16b] is located between the two bearing seats; Four axial loading mechanisms [15] are arranged between the inner end faces of the bearing sleeve [16d]. ] is set on the right-handed screw [15c] through clearance fit, the elastic ring [15a] is placed on one end of the elastic ring backing plate [15b] and set on the right-handed screw [15c], and the polished rod end of the right-handed screw [15c] is inserted In the small hole of the inner end surface of the bearing sleeve [16d], the elastic ring [14a] is close to the inner end surface of the bearing sleeve [16d], and the other end of the right-handed screw rod [14c] is connected to the loading nut [15d] through the right-handed thread ], a number of small holes are set in the middle of the loading nut [15d], the loading rod [15e] is inserted into the small hole in the middle of the loading nut [15d], and one end of the left-handed screw rod [15f] is connected to the loading nut through a left-handed thread The other end of [15d], the other end of the left-handed screw [15f] is sleeved in the force sensor backing plate [15g] through a clearance fit, and the end face of the force sensor [15h] is fixed on the force sensor backing plate [15g] by cross screws, The convex spherical surface at the other end of the force sensor [15h] is abutted in the concave groove of the inner end surface of the bearing sleeve [16d], and the output end of the force sensor [15h] is connected to the input end of the CHB digital display instrument [19]; The optical pen [18] is fixed in the optical pen holding ring [5g], the axis of the optical pen [18] is parallel to the upper surface of the experimental platform [2], and the end face of the optical pen [18] is away from the side convex ring of the rotating shaft [16b] Surface 15~20mm, the output end of optical pen [18] is connected with the input end of CCS type controller [21], the output end of CCS type controller [21] is connected with 24V DC power supply [20], the CCS type controller [ 21] connected to the first computer [22]; The exciter support [12] is located on one side of the experimental platform [2], the exciter [13] is connected to the exciter support [12] through an elastic rope, and the front end of the exciter [13] is connected to the On the impedance head [14], the axis of the impedance head [14] is parallel to the upper plane of the experimental platform [2], the end face of the impedance head [14] is 5 ± 1.5mm from the middle convex ring surface of the rotating shaft [16b], and the acceleration sensor [ 17] The magnetic chuck is placed on the surface of the horizontal radial groove of the bearing sleeve [16d]. The output end of the force signal of the impedance head [14] and the output end of the acceleration sensor [17] are connected with the signal conditioner [23]. The output end of conditioning instrument [23] is connected with the input end of data acquisition device [24], and data acquisition device [24] is connected with second computer [25], and the output end of data acquisition device [24] is connected with power amplifier [26] The input end of the power amplifier [26] is connected to the input end of the exciter [13]. 2. angular contact ball bearing dynamic parameter test experimental device according to claim 1, is characterized in that, the spherical top surface cylinder of displacement gauge lower slider [5b] inner end surface and displacement gauge lower backing plate [5a] outer end surface U-groove clearance fit, the gap between the lower surface of the lower slider [5b] of the displacement gauge and the upper surface of the lower backing plate [5a] of the displacement gauge is 0.5~1mm; the spherical top of the inner end surface of the upper slider [5f] of the displacement gauge The surface cylinder is matched with the U-shaped groove on the outer end surface of the displacement gauge lower backing plate [5e], and the gap between the lower surface of the displacement gauge lower slider [5f] and the upper surface of the displacement gauge lower backing plate [5e] is 0.5~1mm . 3. The experimental device for testing dynamic parameters of angular contact ball bearings according to claim 1, characterized in that the guide flat key [8] and the side of the bottom keyway of the lower bearing housing [6a] are clearance fit, and the fit type is F6/h5 . 4. angular contact ball bearing dynamic parameter testing experimental device according to claim 1, is characterized in that, the upper surface of the experimental platform [2] of displacement meter IPN type damping plate [4], motor IPN type damping plate [9] is installed And the surface roughness of the lower backing plate [5a] of the displacement gauge is in the range of 0.63~1.25μm. 5. The experimental device for testing dynamic parameters of angular contact ball bearings according to claim 1, wherein the number of acceleration sensors [17] is four, and the number of optical pens [18] is two. 6. The experimental device for testing dynamic parameters of angular contact ball bearings according to claim 1, further comprising a leveling shim [1], the number of leveling shims [1] is four, and the four adjustments Flat pad irons [1] are respectively arranged on the four corners below the experimental platform [2].

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