A test bench for detecting a skew angle of a roller of a tapered roller bearing

Abstract

This invention discloses a test bench for detecting the skew angle of tapered roller bearings, comprising a base, and a drive device, a test shaft system, an axial force loading device, a radial force loading device, a torque loading device, a test chamber, and a measurement system mounted on the base. The drive device provides rotational torque to the shaft system. The test shaft system supports and stabilizes the test tapered roller bearing and the bearing under test. The drive device, axial force loading device, radial force loading device, torque loading device, and measurement system are connected in series in the entire test bench. The axial force loading device provides axial force to the test tapered roller bearing and the bearing under test in the test shaft system. This invention can effectively simulate the combined radial force-axial force-torque load state of tapered roller bearings, enabling non-destructive measurement of the skew angle of tapered roller bearings.

Description

Technical Field

[0001] This invention relates to the field of bearing testing technology, specifically to a test bench for testing the skew angle of tapered roller bearings. Background Technology

[0002] Under service conditions, tapered roller bearings are inevitably subject to roller skew due to factors such as bearing structural design, roller eccentricity, manufacturing errors, lubrication methods, and load conditions. Roller skew has an adverse impact on the load-bearing capacity, lubrication, friction, and lifespan of tapered roller bearings. Extensive theoretical and experimental research has been conducted both domestically and internationally to address the roller skew problem in tapered roller bearings. Experimental research primarily focuses on destructive testing, involving secondary machining of the bearing rings to allow sensors to be positioned close to the contact area between the rings and rollers for measuring the skew angle. However, secondary machining of the outer rings inevitably affects the contact state between the rings and rollers, thus impacting the accuracy of the test results. Furthermore, the relevant testing equipment cannot reproduce the combined radial force-axial force-torque load conditions of tapered roller bearings. Summary of the Invention

[0003] The purpose of this invention is to provide a test bench for detecting the roller skew angle of tapered roller bearings, which can simulate the combined load state of radial force, axial force and torque of tapered roller bearings, and carry out non-destructive measurement of the roller skew angle of tapered roller bearings.

[0004] The technical solution adopted in this invention is: a test bench for detecting the skew angle of tapered roller bearings, including a base, and a drive device, a test shaft system, an axial force loading device, a radial force loading device, a torque loading device, a test chamber, and a measurement system disposed on the base; The drive unit is used to provide rotational torque to the test shaft system, driving the test tapered roller bearings and the test tapered roller bearings in the test shaft system to rotate; The test shaft system is used to support and stabilize the test tapered roller bearing and the test tapered roller bearing. The drive device, axial force loading device, radial force loading device, torque loading device, and measurement system are connected in series in the entire test bench. The test shaft system is mounted on the base via the test box. The axial force loading device is used to provide axial force to the test tapered roller bearing and the test tapered roller bearing in the test shaft system; The radial force loading device is used to provide radial force to the test tapered roller bearing and the test tapered roller bearing in the test shaft system; The torque loading device is used to provide torque to the test tapered roller bearing in the test shaft system; The test chamber is used to support and stabilize the test shaft system, axial force loading device and radial force loading device, while also storing lubricating oil and reducing the influence of the external environment on the tested tapered roller bearings in the test shaft system; The measurement system is used to detect the magnitude of the axial force provided by the axial force loading device, the magnitude of the radial force provided by the radial force loading device, the magnitude of the deflection angle of the outer ring of the tested tapered roller bearing, and the magnitude of the roller skew angle of the tested tapered roller bearing.

[0005] As a preferred embodiment, the drive unit includes a servo motor, a flange, and a base; the output shaft of the servo motor and the flange are connected by a flat key or spline, the servo motor and the base are fixed by bolts, and the base and the foundation are fixed by bolts.

[0006] As a preferred embodiment, the test shaft system includes a main shaft, a test tapered roller bearing, a test bearing housing, bushing I, the test tapered roller bearing, the test bearing housing, and bushing II; the main shaft is a multi-stage stepped hollow shaft; the inner rings of the main shaft and the test tapered roller bearing are fixed with an interference fit; the outer ring of the test tapered roller bearing and the test bearing housing are fixed with an interference fit; the outer cylindrical surface of the test bearing housing is a stepped shaft with an annular groove on the end face; the main shaft and bushing I are fixed with a clearance fit; bushing I is used to restrict the axial position of the test tapered roller bearing in the main shaft; the inner rings of the main shaft and the test tapered roller bearing are fixed with an interference fit; the outer ring of the test tapered roller bearing and the test bearing housing are fixed with an interference fit; the outer cylindrical surface of the test bearing housing is spherical; the main shaft and bushing II are fixed with a clearance fit; bushing II is used to restrict the axial position of the test tapered roller bearing in the main shaft; The flanges in the spindle and drive unit are fixed by bolts.

[0007] As a preferred embodiment, the axial force loading device includes an annular loading disk, a cage roller assembly I, an elastic seal ring I, an elastic seal ring II, a tie rod assembly I, a tie rod assembly II, a tie rod assembly III, a tie rod assembly IV, and an axial loading hydraulic cylinder. One end face of the annular loading disk has four grooves evenly distributed circumferentially, the bottom surface of which is inclined circumferentially. The bottom of each groove has an arc-shaped through hole, and the sides of the grooves are all arc-shaped surfaces. The other end face of the annular loading disk has an annular groove, an inner flange, and an outer flange, with sealing grooves on the inner and outer flanges. The cylindrical side of the annular loading disk has an ear plate with slots, the length of which is radial to the annular loading disk. The sealing grooves of the two annular flanges of the annular loading disk are used to install the elastic seal rings I and II. The elastic seal rings I and II are used to seal the cage roller assembly I. The tie rod assembly I includes tie rod I, pressure block I, and nut I; tie rod I is fixed with a clearance fit to the arc-shaped through hole at the bottom of the groove of the annular loading disk; the lower surface of pressure block I is inclined and contacts the bottom surface of the groove of the annular loading disk; the side surface of pressure block I is arc-shaped and is fixed with a clearance fit to the side surface of the groove of the annular loading disk; the upper surface of pressure block I is flat and contacts the nut of tie rod I; tie rod I and nut I are fixed by a threaded connection. The tie rod assembly II includes tie rod II, pressure block II, and nut II; tie rod II is fixed with a clearance fit to the arc-shaped through hole at the bottom of the groove of the annular loading disk; the lower surface of pressure block II is inclined and contacts the bottom surface of the groove of the annular loading disk; the side surface of pressure block II is arc-shaped and is fixed with a clearance fit to the side surface of the groove of the annular loading disk; the upper surface of pressure block II is flat and contacts the nut of tie rod II; tie rod II and nut II are fixed by a threaded connection. The tie rod assembly III includes a tie rod III, a pressure block III, and a nut III. The tie rod III is fixed with a clearance fit to the arc-shaped through hole at the bottom of the groove of the annular loading disk. The lower surface of the pressure block III is an inclined surface that contacts the bottom surface of the groove of the annular loading disk. The side surface of the pressure block III is an arc surface that is fixed with a clearance fit to the side surface of the groove of the annular loading disk. The upper surface of the pressure block III is a flat surface that contacts the nut of the tie rod III. The tie rod III and the nut III are fixed by a threaded connection. The tie rod assembly IV includes tie rod IV, pressure block IV, and nut IV; tie rod IV is fixed with a clearance fit to the arc-shaped through hole at the bottom of the groove of the annular loading disk; the lower surface of pressure block IV is inclined and contacts the bottom surface of the groove of the annular loading disk; the side surface of pressure block IV is arc-shaped and is fixed with a clearance fit to the side surface of the groove of the annular loading disk; the upper surface of pressure block IV is flat and contacts the nut of tie rod IV; tie rod IV and nut IV are fixed by a threaded connection. The parameters of tie rod assembly I, tie rod assembly II, tie rod assembly III, and tie rod assembly IV are completely identical; The cage roller assembly I includes a cage I, rollers I, and flanges I. The cage I has four evenly distributed arc-shaped slots in its circumferential direction, which are respectively fixed with tie rods I, II, III, and IV with clearance fit. Several pockets are evenly distributed between adjacent arc-shaped slots on the cage I, and the surface of the pockets in the circumferential direction of the cage I is an arc surface. The pockets of the cage I are used to install and position rollers I. The pockets of the cage I are fixed with the rollers I with clearance fit. The cage I and flanges I are connected by rivets. Flanges I are used to install and remove rollers I, and to restrict the movement of rollers I in the radial direction of the cage I. The cage roller assembly I is installed in the annular groove on the end face of the test bearing housing and the annular groove on the end face of the annular loading disk. The axially loaded hydraulic cylinder is a structure symmetrical about its central cross-section, including piston rod I, piston I, square cylinder barrel I, square cylinder head I, and square cylinder head II; piston rod I and the annular loading disc lug are fixed with a clearance fit; piston rod I and piston I are fixed by bolts; the square cylinder barrel I is rectangular in shape; a soft seal is used between the square cylinder barrel I and piston I; soft seals are also used between the square cylinder barrel I and square cylinder head I and square cylinder head II, and they are fixed by bolts; square cylinder head I and square cylinder head II have oil ports.

[0008] As a preferred embodiment, the radial force loading device includes a loading rod, a locking nut, a fixed disc, a loading disc, a sealing ring, a cage roller assembly II, a loading bearing housing, and a radial loading hydraulic cylinder; the loading rod and the locking nut are fixed by a threaded connection; the loading rod and the fixed disc are fixed by a key connection; the lower surface of the fixed disc has several fan-shaped surfaces, which are planar in the radial direction and inclined in the circumferential direction; the loading rod and the loading disc are fixed with a clearance fit; the upper surface of the loading disc has several fan-shaped surfaces, which are planar in the radial direction and inclined in the circumferential direction; the cylindrical side of the loading disc has an L-shaped lug with a tapered through hole; the lower surface of the loading disc has an annular groove and an annular flange, the annular flange having a sealing groove; the annular groove of the loading disc is used for installing and positioning the cage roller assembly II; the sealing groove of the loading disc is used for installing the sealing ring; The cage roller assembly II includes a cage II, roller II, and flange II. The cage has a circular through hole at its center, which is fixed to the loading rod with a clearance fit. The cage II has several pockets evenly distributed around its circumference, and the surface of the pockets in the circumferential direction of the cage II is an arc surface. The pockets of the cage II are fixed to the roller II with a clearance fit. The cage II and flange II are connected by rivets. The flange II is used to install and remove the roller II, and to restrict the movement of the roller II in the radial direction of the cage II. The load bearing housing includes cylindrical roller bearing I, cylindrical roller bearing II, a cylindrical bearing housing, retaining ring I, and retaining ring II. Cylindrical roller bearing I is a cylindrical roller bearing with either an inner or outer ring without flanges; its inner ring is fixed to the spindle with an interference fit, and its outer ring is fixed to the cylindrical bearing housing with an interference fit. Cylindrical roller bearing II is a cylindrical roller bearing with either an inner or outer ring without flanges; its inner ring is fixed to the spindle with an interference fit, and its outer ring is fixed to the cylindrical bearing housing with an interference fit. The cylindrical bearing housing is rectangular in shape, and its upper surface and... The loading rod is fixed with bolts; each of the four corners of the cylindrical roller bearing housing has a through hole, which is respectively fixed with tie rod I, tie rod II, tie rod III, and tie rod IV with clearance fit; retaining ring I is used to limit the axial movement of the outer ring of cylindrical roller bearing I and is fixed to the cylindrical roller bearing housing with bolts; retaining ring II is used to limit the axial movement of the outer ring of cylindrical roller bearing II and is fixed to the cylindrical roller bearing housing with bolts; bushing I is used to limit the axial movement of the inner ring of cylindrical roller bearing I; bushing II is used to limit the axial movement of the inner ring of cylindrical roller bearing II. The radially loaded hydraulic cylinder has a symmetrical structure about its central cross-section, including piston rod II, piston II, square cylinder barrel II, square cylinder head III, and square cylinder head IV; piston rod II and loading disc lug are fixed by a tapered through-hole fit; piston rod II and piston II are fixed by bolts; square cylinder barrel II is rectangular in shape and is soft-sealed with piston II; square cylinder barrel II is soft-sealed with square cylinder head III and square cylinder head IV respectively, and is fixed by bolts; square cylinder head III and square cylinder head IV have oil ports.

[0009] As a preferred embodiment, the torque loading device includes a loading shaft assembly, a longitudinal loading seat, a transverse loading seat, a longitudinal moving assembly, a transverse moving assembly, a support assembly, a longitudinal loading hydraulic cylinder, and a transverse loading hydraulic cylinder. The loading shaft assembly includes a loading shaft, a loading flange, a spherical plain bearing, an inner retaining ring, an outer retaining ring I, an outer retaining ring II, and a spherical plain bearing housing. The loading shaft and the loading flange are connected by a spline. The loading flange and the bearing housing under test are fixed by bolts. The loading shaft and the inner ring of the spherical plain bearing are fixed with an interference fit. The loading shaft and the inner retaining ring are fixed by bolts. The inner retaining ring is used to limit the axial movement of the inner ring of the spherical plain bearing. The outer ring of the spherical plain bearing and the bearing housing are fixed with an interference fit. The outer retaining rings I and II are respectively fixed to the bearing housing by bolts. The outer retaining rings I and II are used to limit the axial movement of the outer ring of the spherical plain bearing. The bearing housing has a cross-shaped structure with protruding limiting blocks in the longitudinal and transverse directions. The longitudinal loading seat includes frame I and frame II; frame I and frame II have the same structure and are fixed by bolts; the longitudinal loading seat composed of frame I and frame II is fixed to the longitudinal limiting block of the spherical bearing seat with clearance fit; The transverse loading seat includes frame III and frame IV; frame III and frame IV have the same structure and are fixed by bolts; the transverse loading seat composed of frame III and frame IV is fixed to the transverse limiting block of the spherical bearing seat with clearance fit; the longitudinal loading seat passes through the transverse loading seat and is fixed to the transverse loading seat with clearance fit. The longitudinal movement assembly includes slider group I, guide rail group I, stop group I, slider group II, guide rail group II, and stop group II; the outer side of frame III is fixed to slider group I by bolts and slides on guide rail group I via slider group I; stop group I is used to limit the ultimate displacement of slider group I; the outer side of frame IV is fixed to slider group II by bolts and slides on guide rail group II via slider group II; stop group II is used to limit the ultimate displacement of slider group II. The lateral movement assembly includes slider group III, guide rail group III, stop group III, slider group IV, guide rail group IV, and stop group IV; the outer side of frame I is fixed to slider group III by bolts and slides on guide rail group III via slider group III; stop group III is used to limit the ultimate displacement of slider group III; the outer side of frame II is fixed to slider group IV by bolts and slides on guide rail group IV via slider group IV; stop group IV is used to limit the ultimate displacement of slider group IV; The support assembly includes a front support, a column assembly, and a rear support; the front support and the base are fixed together by bolts; the front support is connected to the rear support via the column assembly, and the front support, column assembly, and rear support are fixed together by bolts; the rear support and the base are fixed together by bolts; the front support and guide rail assembly I are fixed together by bolts; the front support and stop block assembly I are fixed together by bolts; the front support and guide rail assembly III are fixed together by bolts; the front support and stop block assembly III are fixed together by bolts; the rear support and guide rail assembly II are fixed together by bolts; the rear support and guide rail assembly II are fixed together by bolts; the rear support and stop block assembly IV are fixed together by bolts. The longitudinal loading hydraulic cylinder includes piston assembly I, loading block I, circular cylinder barrel I, circular cylinder head I, guide sleeve I, and circular cylinder bottom I; the piston rod of piston assembly I and loading block I are fixed by bolts; loading block I and spherical bearing seat are fixed by bolts; there is a soft seal between the piston of piston assembly I and circular cylinder barrel I; there is a soft seal between circular cylinder barrel I and circular cylinder head I; circular cylinder barrel I, circular cylinder head I, and frames I and II of the longitudinal loading seat are fixed by bolts; there is a soft seal between circular cylinder barrel I and circular cylinder bottom I, and they are also fixed by bolts. The transverse loading hydraulic cylinder includes piston assembly II, loading block II, circular cylinder barrel II, circular cylinder head II, guide sleeve II, and circular cylinder bottom II; the piston rod of piston assembly II and loading block II are fixed by bolts; loading block II and spherical bearing seat are fixed by bolts; there is a soft seal between the piston of piston assembly II and circular cylinder barrel II; there is a soft seal between circular cylinder barrel II and circular cylinder head II; circular cylinder barrel II, circular cylinder head II, and frames III and IV of the transverse loading seat are fixed by bolts; there is a soft seal between circular cylinder barrel II and circular cylinder bottom II, and they are fixed by bolts.

[0010] As a preferred embodiment, the test chamber includes a front plate, a rear plate, a cover plate, a left side plate, a right side plate I, and a right side plate II; the front plate is fixed to the base, the cover plate, the left side plate, the right side plate I, and the right side plate II by bolts; the rear plate is fixed to the base, the cover plate, the left side plate, the right side plate I, and the right side plate II by bolts; the cover plate is fixed to the square cylinder I of the axial loading hydraulic cylinder by bolts; the cover plate is fixed to the square cylinder II of the radial loading hydraulic cylinder by bolts; the upper surface of the cover plate has an annular groove for installing and positioning the cage roller assembly II; the cover plate has a through hole concentric with the annular groove for installing and positioning the loading rod; the upper surface of the cover plate contacts the sealing ring; the cover plate, the sealing ring, and the loading disc form a sealed space, which seals the cage roller assembly II; The left side plate has a stepped hole in the center for mounting the test bearing housing and guiding its axial movement; the left side plate and the base are fixed together with bolts; the right side plate I has two through holes for mounting tie rod I and tie rod II, and is fixed with tie rod I and tie rod II with clearance fit; the right side plate I has a concave spherical surface for mounting and positioning the outer spherical surface of the test bearing housing, and the concave spherical surface of the right side plate I has a rectangular groove in the middle; the right side plate II has two through holes for mounting tie rod III and tie rod IV, and is fixed with tie rod III and tie rod IV with clearance fit; the right side plate II has a concave spherical surface for mounting and positioning the outer spherical surface of the test bearing housing; the right side plate II and the base are fixed together with bolts; the right side plate I, the right side plate II, and the test bearing housing together form a spherical bearing.

[0011] As a preferred embodiment, the measurement system includes pressure sensor I, pressure sensor II, pressure sensor III, pressure sensor IV, pressure sensor V, longitudinal displacement sensor, lateral displacement sensor, ultrasonic transmitter and receiver I, and ultrasonic transmitter and receiver II. Pressure sensors I, II, III, IV, and V are all annular hollow force sensors. Pressure sensor I is fixed to pull rod I with a clearance fit and connected in series between right side plate I and nut I. Pressure sensor II is fixed to pull rod II with a clearance fit and connected in series between right side plate II and nut II. Pressure sensor III is fixed to pull rod III with a clearance fit and connected in series between right side plate II and nut III. Pressure sensor IV is fixed to pull rod IV with a clearance fit and connected in series between right side plate I and nut IV. Pressure sensor V is fixed to load rod with a clearance fit and connected in series between locking nut and fixed disc. Both the longitudinal and lateral displacement sensors are rod-type displacement sensors; the rod of the longitudinal displacement sensor and the longitudinal limiting block of the spherical bearing housing are fixed by threaded connection; the housing flange of the longitudinal displacement sensor and the frame I and frame II of the longitudinal loading seat are fixed by bolts; the rod of the lateral displacement sensor and the lateral limiting block of the spherical bearing housing are fixed by threaded connection; the housing flange of the lateral displacement sensor and the frame III and frame IV of the lateral loading seat are fixed by bolts. Ultrasonic transmitter-receiver I and ultrasonic transmitter-receiver II are used to measure the roller skew angle of the tested tapered roller bearing. The measurement principle involves two ultrasonic beams emitted by the transmitter reflecting off the roller surface of the tested tapered roller bearing and returning to the receiver. The skew angle is calculated based on the time difference between the round trip of the two ultrasonic beams and the roller rotation speed. Ultrasonic transmitter-receiver I is used to transmit ultrasonic signals to the small end surface of the tested tapered roller bearing and to receive the ultrasonic signals reflected from the small end surface. Ultrasonic transmitter-receiver I is installed in a groove in the bearing housing and is threadedly connected to the bearing housing. Ultrasonic transmitter-receiver II is used to transmit ultrasonic signals to the large end surface of the tested tapered roller bearing and to receive the ultrasonic signals reflected from the large end surface. Ultrasonic transmitter-receiver II is also installed in a groove in the bearing housing and is threadedly connected to the bearing housing. Ultrasonic transmitter-receiver I and ultrasonic transmitter-receiver II are located in the same axial plane of the tested tapered roller bearing.

[0012] Compared with the prior art, the beneficial effects of the present invention are: This invention enables non-destructive testing of the roller skew angle of tapered roller bearings under simulated radial force-axial force-torque combined load conditions. It provides an experimental platform for the fundamental theoretical research of tapered roller bearings, helps to evaluate the kinematic state of the rollers during service, and verifies the accuracy and rationality of the design parameters of tapered roller bearings. Attached Figure Description

[0013] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0014] Figure 1 This is a schematic diagram of the overall structure of the present invention; Figure 2 This is a schematic diagram of the drive device structure of the present invention; Figure 3 This is a schematic diagram of the shaft system structure of the present invention; Figure 4 This is a schematic diagram of the transverse structure of the axial force loading device in this invention; Figure 5 This is a schematic diagram of the longitudinal structure of the axial force loading device in this invention; Figure 6 This is a cross-sectional view of the radial force loading device in this invention; Figure 7 This is a partial structural schematic diagram of the radial force loading device in this invention; Figure 8 This is a schematic diagram of the torque loading device of the present invention; Figure 9 This is a cross-sectional schematic diagram of the loading shaft assembly in this invention; Figure 10 for Figure 9 A cross-sectional diagram; Figure 11 This is a schematic diagram of the structure of the moving component in this invention; Figure 12 This is a schematic diagram of the test chamber in this invention.

[0015] Reference numerals: 1-Base; 2-Drive device; 3-Test shaft system; 4-Axial force loading device; 5-Radial force loading device; 6-Torque loading device; 7-Test chamber; 8-Measuring system; 21-Servo motor; 22-Flange; 23-Base; 31-Main shaft; 32-Tested tapered roller bearing; 33-Tested bearing housing; 34-Sleeve I; 35-Tested tapered roller bearing; 36-Tested bearing housing; 37-Sleeve II; 41-Annular loading disc; 42-Cage roller assembly I; 421-Cage I; 422-Roll I; 423-Flange I; 43-Elastic seal I; 44-Elastic seal II; 45-Tie rod assembly I; 451-Tie rod I; 452-Pressure block I; 453-Nut I; 46 - Tie rod assembly II; 461- Tie rod II; 462- Pressure block II; 463- Nut II; 47- Tie rod assembly III; 471- Tie rod III; 472- Pressure block III; 473- Nut III; 48- Tie rod assembly IV; 481- Tie rod IV; 482- Pressure block IV; 483- Nut IV; 49- Axial loading hydraulic cylinder; 491- Piston rod; 492- Piston I; 493- Square cylinder I; 494- Square cylinder head I; 495- Square cylinder head II; 51- Loading rod; 52- Locking nut; 53- Fixed disc; 54- Loading disc; 55- Sealing ring; 56- Cage roller assembly II; 561- Cage II; 562- Roller II; 563- Flange II; 57- Loading bearing housing; 571- Cylindrical roller bearing I; 572-Cylindrical roller bearing II; 573-Cylindrical bearing housing; 574-Retaining ring I; 575-Retaining ring II; 58-Radial loading hydraulic cylinder; 581-Piston rod II; 582-Piston II; 583-Square cylinder barrel II; 584-Square cylinder head III; 585-Square cylinder head IV; 61-Loading shaft assembly; 611-Loading shaft; 612-Loading flange; 613-Spherical plain bearing; 614-Inner retaining ring; 615-Outer retaining ring I; 616-Outer retaining ring II; 617-Spherical plain bearing housing; 62-Longitudinal loading seat; 621-Frame I; 622-Frame II; 63-Transverse loading seat; 631-Frame III; 632-Frame IV; 64-Longitudinal moving assembly; 641-Slider assembly I; 642-Guide rail assembly I; 6 43-Stop assembly I; 644-Slider assembly II; 645-Guide rail assembly II; 646-Stop assembly II; 65-Transverse movement assembly; 651-Slider assembly III; 652-Guide rail assembly III; 653-Stop assembly III; 654-Slider assembly IV; 655-Guide rail assembly IV; 656-Stop assembly IV; 66-Bracket assembly; 661-Front bracket; 662-Column assembly; 663-Rear bracket; 67-Longitudinal loading hydraulic cylinder; 671-Piston assembly I; 672-Loading block I; 673-Circular cylinder barrel I; 674-Circular cylinder head I; 675-Guide sleeve I; 676-Circular cylinder bottom I; 68-Transverse loading hydraulic cylinder; 681-Piston assembly II; 682-Loading block II; 683-Circular cylinder barrel II; 684-Circular cylinder head II;685-Guide sleeve II; 686-Circular cylinder bottom II; 71-Front plate; 72-Rear plate; 73-Cover plate; 74-Left side plate; 75-Right side plate I; 76-Right side plate II; 81-Pressure sensor I; 82-Pressure sensor II; 83-Pressure sensor III; 84-Pressure sensor IV; 85-Pressure sensor V; 86-Longitudinal displacement sensor; 87-Lateral displacement sensor; 88-Ultrasonic transmitter and receiver I; 89-Ultrasonic transmitter and receiver II. Detailed Implementation

[0016] The present invention will now be described in detail through exemplary embodiments. However, it should be understood that, without further description, elements, structures, and features in one embodiment may be advantageously incorporated into other embodiments.

[0017] It should be noted that, unless otherwise defined, the technical or scientific terms used herein should have the ordinary meaning understood by one of ordinary skill in the art to which this invention pertains. The terms "a," "an," or "the," etc., used in the specification and claims of this patent application do not express a limitation on quantity, but rather indicate the presence of at least one; the terms "first," "second," and "third," as used herein, should not be considered as a limitation on the order of components, but are merely for distinguishing different components; the terms "comprising," "including," etc., indicate that the elements or objects preceding "comprising" or "including" encompass the elements or objects listed following "comprising" or "including" and their equivalents, but do not exclude other elements or objects having the same function.

[0018] To more clearly describe this tapered roller bearing roller skew angle testing bench, in conjunction with the attached... Figure 1-12 This embodiment is described as follows: like Figure 1-12 As shown, a test bench for detecting the skew angle of tapered roller bearings is provided. The invention concept is as follows: The test tapered roller bearing and the test tapered roller bearing are mounted in pairs on the main shaft. A axial force load and a radial force load are applied to the two sets of bearings using a tie rod loading method, and a torque load is applied to the test tapered roller bearing using a lever loading method. The axial force load is powered by hydraulic pressure, which tensions the axial tie rod assembly. The tension force is transmitted from the test tapered roller bearing to the test tapered roller bearing via the main shaft. The radial force load is also powered by hydraulic pressure, which tensions the radial tie rod assembly. The tension force is transmitted to the main shaft via the loading bearing housing and evenly distributed between the test and test tapered roller bearings. A pair of cylindrical roller bearings provide slewing support between the radial tie rod assembly and the main shaft. The moment load is powered by two hydraulic cylinders arranged longitudinally and laterally. The hydraulic cylinders output hydraulic pressure to apply a bending moment load to the loading shaft (lever), which is then transmitted to the test tapered roller bearing via the loading shaft, creating a moment load on the test tapered roller bearing. These loads can be applied simultaneously, thus simulating the combined radial force-axial force-moment load state of the tapered roller bearing. The roller skew angle of tapered roller bearings is measured using ultrasonic methods to achieve non-destructive measurement of the roller skew angle under different load conditions.

[0019] Based on the above concept, the testing bench of the present invention comprises eight parts: a base 1, a driving device 2, a test shaft system 3, an axial force loading device 4, a radial force loading device 5, a torque loading device 6, a test chamber 7, and a measurement system 8. The drive unit 2 provides rotational torque to the test shaft system 3, driving the test tapered roller bearings and the test tapered roller bearings in the test shaft system 3 to rotate. The test shaft system 3 supports and stabilizes the test tapered roller bearings and the test tapered roller bearings. The drive unit 2, axial force loading device 4, radial force loading device 5, torque loading device 6, and measuring system 8 are connected in series in the entire test bench. The test shaft system 3 is mounted on the base 1 via the test chamber 7. The axial force loading device 4 provides axial force to the test tapered roller bearings and the test tapered roller bearings in the test shaft system 3. The radial force loading device 5 provides radial force to the test tapered roller bearings and the test tapered roller bearings in the test shaft system 3. The torque loading device 6 provides torque to the test tapered roller bearings in the test shaft system 3. The test chamber 7 supports and stabilizes the test shaft system 3, the axial force loading device 4, and the radial force loading device 5, and can also store lubricating oil and reduce the influence of the external environment on the test tapered roller bearings in the test shaft system 3. The measuring system 8 is used to detect the magnitude of the axial force provided by the axial force loading device 4, the magnitude of the radial force provided by the radial force loading device 5, the magnitude of the deflection angle of the outer ring of the tested tapered roller bearing, and the magnitude of the roller skew angle of the tested tapered roller bearing.

[0020] The following provides a detailed description of the structural form, positional relationship, and assembly relationship of the seven parts excluding the base.

[0021] like Figure 1 and 2 As shown, the drive device 2 includes a servo motor 21, a flange 22, and a base 23; the output shaft of the servo motor 21 and the flange 22 are connected by a flat key or spline; the servo motor 21 and the base 23 are fixed by bolts; the base 23 and the base 1 are fixed by bolts.

[0022] like Figure 3 As shown, the test shaft system 3 includes a main shaft 31, a test tapered roller bearing 32, a test bearing housing 33, bushing I 34, a test tapered roller bearing 35, a test bearing housing 36, and bushing II 37; the main shaft 31 is a multi-stage stepped hollow shaft; the inner rings of the main shaft 31 and the test tapered roller bearing 32 are fixed with an interference fit; the outer ring of the test tapered roller bearing 32 and the test bearing housing 33 are fixed with an interference fit; the outer cylindrical surface of the test bearing housing 33 is a stepped shaft with an annular groove on the end face; the main shaft 31 The test tapered roller bearing 32 is fixed with a clearance fit to the inner ring of the test tapered roller bearing 35. The outer ring of the test tapered roller bearing 35 is fixed with an interference fit to the test bearing housing 36. The outer surface of the test bearing housing 36 is spherical. The test shaft 31 and the test sleeve II 37 are fixed with a clearance fit. The test sleeve II 37 is used to limit the axial position of the test tapered roller bearing 35 in the main shaft 31.

[0023] like Figure 2 and Figure 3 As shown, the spindle 31 and the flange 22 in the drive unit 2 are fixed by bolts.

[0024] like Figure 2 and Figure 3 As shown, the transmission path of the speed and torque provided by the drive device 2 is as follows: First, the servo motor 21 is started and outputs speed and torque. Then, the speed and torque are output from the servo motor 21 to the spindle 31 via the flange 22. Under the premise that the output torque overcomes the frictional torque of the test tapered roller bearing 32 and the test tapered roller bearing 35, the inner rings of the test tapered roller bearing 32 and the test tapered roller bearing 35 will be driven to rotate.

[0025] like Figure 4 and Figure 5As shown, the axial force loading device 4 includes an annular loading disk 41, a cage roller assembly I 42, an elastic sealing ring I 43, an elastic sealing ring II 44, a tie rod assembly I 45, a tie rod assembly II 46, a tie rod assembly III 47, a tie rod assembly IV 48, and an axial loading hydraulic cylinder 49. One end face of the annular loading disk 41 has four grooves evenly distributed in the circumferential direction. The bottom surface of the grooves is inclined in the circumferential direction, and the bottom of the grooves has an arc-shaped through hole. The sides of the grooves are all arc surfaces. The other end face of the annular loading disk 41 has an annular groove, an inner flange, and an outer flange. The inner flange and the outer flange have sealing grooves. The cylindrical side of the annular loading disk 41 has an ear plate with a slot. The length direction of the slot is the radial direction of the annular loading disk 41. The sealing grooves of the two annular flanges of the annular loading disk 41 are used to install the elastic sealing rings I 43 and II 44. The elastic sealing rings I 43 and II 44 are used to seal the cage roller assembly I 42. The pull rod assembly I 45 includes a pull rod I 451, a pressure block I 452, and a nut I 453; the pull rod I 451 is fixed with a clearance fit to the arc-shaped through hole at the bottom of the groove of the annular loading disk 41; the lower surface of the pressure block I 452 is an inclined surface, which contacts the bottom surface of the groove of the annular loading disk 41; the side surface of the pressure block I 452 is an arc surface, which is fixed with a clearance fit to the side surface of the groove of the annular loading disk 41; the upper surface of the pressure block I 451 is a flat surface, which contacts the nut of the pull rod I 451; the pull rod I 451 and the nut I 453 are fixed by a threaded connection. The pull rod assembly II 46 includes a pull rod II 461, a pressure block II 462, and a nut II 463; the pull rod II 461 is fixed with a clearance fit to the arc-shaped through hole at the bottom of the groove of the annular loading disk 41; the lower surface of the pressure block II 462 is an inclined surface, which contacts the bottom surface of the groove of the annular loading disk 41; the side surface of the pressure block II 462 is an arc surface, which is fixed with a clearance fit to the side surface of the groove of the annular loading disk 41; the upper surface of the pressure block II 461 is a flat surface, which contacts the nut of the pull rod II 461; the pull rod II 461 and the nut II 463 are fixed by a threaded connection. The pull rod assembly Ⅲ47 includes a pull rod Ⅲ471, a pressure block Ⅲ472, and a nut Ⅲ473; the pull rod Ⅲ471 is fixed with a clearance fit to the arc-shaped through hole at the bottom of the groove of the annular loading disk 41; the lower surface of the pressure block Ⅲ472 is an inclined surface, which contacts the bottom surface of the groove of the annular loading disk 41; the side surface of the pressure block Ⅲ472 is an arc surface, which is fixed with a clearance fit to the side surface of the groove of the annular loading disk 41; the upper surface of the pressure block Ⅲ471 is a flat surface, which contacts the nut of the pull rod Ⅲ471; the pull rod Ⅲ471 and the nut Ⅲ473 are fixed by a threaded connection. The pull rod assembly IV48 includes a pull rod IV481, a pressure block IV482, and a nut IV483; the pull rod IV481 is fixed with a clearance fit to the arc-shaped through hole at the bottom of the groove of the annular loading disk 41; the lower surface of the pressure block IV482 is an inclined surface, which contacts the bottom surface of the groove of the annular loading disk 41; the side surface of the pressure block IV482 is an arc surface, which is fixed with a clearance fit to the side surface of the groove of the annular loading disk 41; the upper surface of the pressure block IV481 is a flat surface, which contacts the nut of the pull rod IV481; the pull rod IV481 and the nut IV483 are fixed by a threaded connection. The parameters of tie rod assembly I 45, tie rod assembly II 46, tie rod assembly III 47 and tie rod assembly IV 48 are completely identical; The cage roller assembly I42 includes a cage I421, a roller I422, and a flange I423. The cage I421 has four evenly distributed arc-shaped slots in its circumferential direction, which are respectively fixed with tie rods I451, II461, III471, and IV481 with clearance fit. Several pockets are evenly distributed between adjacent arc-shaped slots on the cage I421, and the surface of the pockets in the circumferential direction of the cage I421 is an arc surface. The pockets of the cage I421 are used to install and position the roller I422. The pockets of the cage I421 and the roller I422 are fixed with clearance fit. The cage I421 and the flange I423 are connected by rivets. The flange I423 is used to install and remove the roller I422, and to restrict the movement of the roller I422 in the radial direction of the cage I421. The axially loaded hydraulic cylinder 49 is a symmetrical structure about its central cross-section, including piston rod I 491, piston I 492, square cylinder I 493, square cylinder head I 494, and square cylinder head II 495; piston rod I 491 and the ear plate of the annular loading disk 41 are fixed with a clearance fit; piston rod I 491 and piston I 492 are fixed by bolts; the square cylinder I 493 is rectangular; a soft seal is used between the square cylinder I 493 and piston I 492; soft seals are also used between the square cylinder I 493 and square cylinder heads I 494 and II 495, and they are fixed by bolts; square cylinder heads I 494 and II 495 have oil ports.

[0026] like Figures 3-5 As shown, the cage roller assembly I 42 is installed in the annular groove on the end face of the test bearing housing 33 and the annular groove on the end face of the annular loading disk 41.

[0027] like Figures 3-5As shown, the specific loading process of the axial force is as follows: First, before loading the axial force, pre-tighten nuts I453, II463, III473 and IV483 appropriately to make the readings of pressure sensors I81, II82, III83 and IV84 equal, so as to ensure that the tension of tie rods I451, II461, III471 and IV481 is the same. Then, the hydraulic pressure at the inlet and outlet of the axial loading hydraulic cylinder 49 is controlled, causing piston I 492 to move along the square cylinder I 493 with piston rod I 491. During the movement, piston rod I 491 contacts the lug of the annular loading disk 41, causing the annular loading disk 41 to rotate relative to the test bearing seat 33, as well as the tie rods I 451, II 461, III 471, and IV 481. Simultaneously, this causes the pressure blocks I 452, II 462, III 472, and IV 482 to slide along the four grooves of the annular loading disk 41. Since the bottoms of the four grooves are all inclined surfaces, each pressure block will... The system slides along the inclined plane at the bottom of each groove from the bottom to the top of the inclined plane, further tensioning tie rods I 451, II 461, III 471, and IV 481 during this process. Under the tension of each tie rod, the test bearing housing 33 will move closer to the test bearing housing 33 along the axial direction of the main shaft 31. The tension of each tie rod will be transmitted sequentially from the test bearing housing 33, the test tapered roller bearing 32, bushing I 34, the main shaft 31, bushing II 37, and the test tapered roller bearing 35 to the test bearing housing 36, thereby completing the axial force loading on the test tapered roller bearing 32 and the test tapered roller bearing 35. Finally, when the sum of the readings of pressure sensors I 81, II 82, III 83, and IV 84 reaches the expected value, the axial loading hydraulic cylinder 49 stops pressurizing and maintains pressure. During axial force loading, the cage roller assembly I 42 acts as a rotational support between the annular loading disk 41 and the test bearing housing 33.

[0028] like Figure 6 and Figure 7As shown, the radial force loading device 5 includes a loading rod 51, a locking nut 52, a fixed disc 53, a loading disc 54, a sealing ring 55, a cage roller assembly II 56, a loading bearing seat 57, and a radial loading hydraulic cylinder 58; the loading rod 51 and the locking nut 52 are fixed by a threaded connection; the loading rod 51 and the fixed disc 53 are fixed by a key connection; the lower surface of the fixed disc 53 has several fan-shaped surfaces, which are planar in the radial direction and inclined in the circumferential direction; the loading rod 51 and The loading disc 54 is fixed with a clearance fit; the upper surface of the loading disc 54 has several fan-shaped surfaces, which are flat in the radial direction and inclined in the circumferential direction; the cylindrical side of the loading disc 54 has L-shaped lugs with tapered through holes; the lower surface of the loading disc 54 has an annular groove and an annular flange, with a sealing groove on the annular flange; the annular groove of the loading disc 54 is used to install and position the cage roller assembly II 56; the sealing groove of the loading disc 54 is used to install the sealing ring 55. The cage roller assembly II 56 includes a cage II 561, a roller II 562, and a flange II 563. The cage II 561 has a circular through hole at its center, which is fixed to the loading rod 51 with a clearance fit. The cage II 561 has several pockets evenly distributed around its circumference, and the surface of the pockets in the circumferential direction of the cage II 561 is an arc surface. The pockets of the cage II 561 are fixed to the roller II 562 with a clearance fit. The cage II 561 and the flange II 563 are connected by rivets. The flange II 563 is used to install and remove the roller II 562, and to restrict the movement of the roller II 562 in the radial direction of the cage II 561. The load bearing housing 57 includes cylindrical roller bearing I 571, cylindrical roller bearing II 572, cylindrical bearing housing 573, retaining ring I 574, and retaining ring II 575; cylindrical roller bearing I 571 is a cylindrical roller bearing with no inner ring or no outer ring, and its outer ring is fixed to the cylindrical bearing housing 573 with an interference fit; cylindrical roller bearing II 572 is a cylindrical roller bearing with no inner ring or no outer ring, and its outer ring is fixed to the cylindrical bearing housing 573 with an interference fit. The cylindrical bearing housing 573 is rectangular in shape, with a through hole at each of its four corners. The upper surface of the cylindrical bearing housing 573 and the loading rod 51 are fixed together by bolts. The retaining ring I 574 is used to limit the axial movement of the outer ring of the cylindrical roller bearing I 571 and is fixed together with the cylindrical bearing housing 573 by bolts. The retaining ring II 575 is used to limit the axial movement of the outer ring of the cylindrical roller bearing II 572 and is fixed together with the cylindrical bearing housing 573 by bolts. The radially loaded hydraulic cylinder 58 has a symmetrical structure about its central cross-section, including piston rod II 581, piston II 582, square cylinder barrel II 583, square cylinder head III 584, and square cylinder head IV 585; piston rod II 581 and the loading disc 54 are fixed by a tapered through-hole fit; piston rod II 581 and piston II 582 are fixed by bolts; the square cylinder barrel II 583 is rectangular and is soft-sealed with piston II 582; the square cylinder barrel II 583 is soft-sealed with square cylinder head III 584 and square cylinder head IV 585 respectively, and is fixed by bolts; square cylinder head III 584 and square cylinder head IV 585 are equipped with oil ports.

[0029] like Figure 3 , Figure 5 and Figure 6 As shown, the inner ring of cylindrical roller bearing I 571 is fixed to the main shaft 31 with an interference fit; bushing I 34 is used to restrict the axial movement of the inner ring of cylindrical roller bearing I 571; the inner ring of cylindrical roller bearing II 572 is fixed to the main shaft 31 with an interference fit; bushing II 37 is used to restrict the axial movement of the inner ring of cylindrical roller bearing II 572.

[0030] like Figure 3 , Figure 5 , Figure 6 and Figure 7As shown, the specific loading process of the radial force is as follows: First, the hydraulic pressure at the inlet and outlet of the radial loading hydraulic cylinder 58 is controlled, causing piston II 582 to move along the square cylinder II 583 with piston rod II 581. During the movement, piston rod II 581 contacts the lug of the loading disk 54, causing the loading disk 54 to rotate relative to the loading rod 51, the fixed disk 53, and the loading bearing seat 57. Since the lower surface of the fixed disk 53 is a number of circumferentially inclined fan-shaped surfaces, and the upper surface of the loading disk 54 is a number of circumferentially inclined fan-shaped surfaces, the axial distance between the fixed disk 53 and the loading disk 54 increases when they rotate relative to each other, thereby tensioning the loading rod 51. The tension force of the loading rod 51... Under the action of the loading rod 51, the loading bearing housing 57 will move radially along the main shaft 31. During this process, the tension force of the loading rod 51 will be transmitted from the loading rod 51 to the cylindrical bearing housing 573, and then transmitted to the main shaft via the cylindrical roller bearing I 571 and the cylindrical roller bearing II 572. Then, it will be transmitted to the test bearing housing 33 and the test bearing housing 36 via the test tapered roller bearing 32 and the test tapered roller bearing 35, respectively, thereby completing the radial force loading on the test tapered roller bearing 32 and the test tapered roller bearing 35. Since the test tapered roller bearing 32 and the test tapered roller bearing 35 are symmetrically arranged at both ends of the loading bearing housing 57, the tension force of the loading rod 51 will be evenly distributed to the test tapered roller bearing 32 and the test tapered roller bearing 35. Finally, when the reading of pressure sensor V85 reaches the expected value, the radial loading hydraulic cylinder 58 stops pressurizing and maintains pressure; half of the reading of pressure sensor V85 is the radial force applied to the tested tapered roller bearing 35; during the radial force loading process, the cage roller assembly II 56 plays the role of rotational support between the loading disk 54 and the cover plate 73.

[0031] like Figures 4-7 As shown, the four through holes on the cylindrical bearing housing 573 are respectively fixed with tie rod I 451, tie rod II 461, tie rod III 471, and tie rod IV 481 with clearance fit.

[0032] like Figures 8-11 As shown, the torque loading device 6 includes a loading shaft assembly 61, a longitudinal loading seat 62, a transverse loading seat 63, a longitudinal moving assembly 64, a transverse moving assembly 65, a support assembly 66, a longitudinal loading hydraulic cylinder 67, and a transverse loading hydraulic cylinder 68. The loading shaft assembly 61 includes a loading shaft 611, a loading flange 612, a spherical plain bearing 613, an inner retaining ring 614, an outer retaining ring I 615, an outer retaining ring II 616, and a spherical plain bearing housing 617. The loading shaft 611 and the loading flange 612 are connected by a spline. The loading shaft 611 and the inner ring of the spherical plain bearing 613 are fixed with an interference fit. The loading shaft 611 and the inner retaining ring 614 are fixed with bolts. The inner retaining ring 614 is used to limit the axial movement of the inner ring of the spherical plain bearing 613. The outer ring of the spherical plain bearing 613 and the spherical plain bearing housing 617 are fixed with an interference fit. The outer retaining rings I 615 and II 616 are fixed to the spherical plain bearing housing 617 with bolts. The outer retaining rings I 615 and II 616 are used to limit the axial movement of the outer ring of the spherical plain bearing 613. The spherical plain bearing housing 617 has a cross-shaped structure with protruding limiting blocks in the longitudinal and transverse directions. The longitudinal loading seat 62 includes frame I 621 and frame II 622; frame I 621 and frame II 622 have the same structure and are fixed by bolts; the longitudinal loading seat 62 composed of frame I 621 and frame II 622 is fixed to the longitudinal limiting block of the spherical bearing seat 617 with clearance fit. The transverse loading seat 63 includes frame III 631 and frame IV 632; frame III 631 and frame IV 632 have the same structure and are fixed by bolts; the transverse loading seat 63 composed of frame III 631 and frame IV 632 is fixed to the transverse limiting block of the spherical bearing seat 617 with clearance fit; the longitudinal loading seat 62 passes through the transverse loading seat 63 and is fixed to the transverse loading seat 63 with clearance fit. The longitudinal movement assembly 64 includes slider group I 641, guide rail group I 642, stop group I 643, slider group II 644, guide rail group II 645, and stop group II 646; the outer side of frame III 631 is fixed to slider group I 641 by bolts and slides on guide rail group I 642 via slider group I 641; stop group I 643 is used to limit the ultimate displacement of slider group I 641; the outer side of frame IV 632 is fixed to slider group II 644 by bolts and slides on guide rail group II 645 via slider group II 644; stop group II 646 is used to limit the ultimate displacement of slider group II 644. The lateral movement assembly 65 includes slider group III 651, guide rail group III 652, stop group III 653, slider group IV 654, guide rail group IV 655, and stop group IV 656. The outer side of frame I 621 is fixed to slider group III 651 by bolts and slides on guide rail group III 652 via slider group III 651. Stop group III 653 is used to limit the ultimate displacement of slider group III 651. The outer side of frame II 622 is fixed to slider group IV 654 by bolts and slides on guide rail group IV 655 via slider group IV 654. Stop group IV 656 is used to limit the ultimate displacement of slider group IV 654. The support assembly 66 includes a front support 661, a column assembly 662, and a rear support 663. The front support 661 and the base 1 are fixed together by bolts. The front support 661 is connected to the rear support 663 via the column assembly 662, and the front support 661, column assembly 662, and rear support 663 are fixed together by bolts. The rear support 663 and the base 1 are fixed together by bolts. The front support 661 and guide rail assembly I 642 are fixed together by bolts. The front support 661 and stop block assembly I 643 are fixed together by bolts. The front support 661 and guide rail assembly III 652 are fixed together by bolts. The front support 661 and stop block assembly III 653 are fixed together by bolts. The rear support 663 and guide rail assembly II 645 are fixed together by bolts. The rear support 663 and stop block assembly II 646 are fixed together by bolts. The rear support 663 and guide rail assembly IV 655 are fixed together by bolts. The rear support 663 and stop block assembly IV 656 are fixed together by bolts. The longitudinal loading hydraulic cylinder 67 includes a piston assembly I 671, a loading block I 672, a circular cylinder barrel I 673, a circular cylinder head I 674, a guide sleeve I 675, and a circular cylinder bottom I 676; the piston rod of the piston assembly I 671 and the loading block I 672 are fixed by bolts; the loading block I 672 and the spherical bearing seat 617 are fixed by bolts; a soft seal is used between the piston of the piston assembly I 671 and the circular cylinder barrel I 673; a soft seal is used between the circular cylinder barrel I 673 and the circular cylinder head I 674; the circular cylinder barrel I 673, the circular cylinder head I 674, and the frames I 621 and II 622 of the longitudinal loading seat 62 are fixed by bolts; a soft seal is used between the circular cylinder barrel I 673 and the circular cylinder bottom I 676, and they are also fixed by bolts. The transverse loading hydraulic cylinder 68 includes a piston assembly II 681, a loading block II 682, a circular cylinder barrel II 683, a circular cylinder head II 684, a guide sleeve II 685, and a circular cylinder bottom II 686. The piston rod of the piston assembly II 681 and the loading block II 682 are fixed by bolts. The loading block II 682 and the spherical bearing seat 617 are fixed by bolts. There is a soft seal between the piston of the piston assembly II 681 and the circular cylinder barrel II 683. There is a soft seal between the circular cylinder barrel II 683 and the circular cylinder head II 684. The circular cylinder barrel II 683, the circular cylinder head II 684, and the frames III 631 and IV 632 of the transverse loading seat 63 are fixed by bolts. There is a soft seal between the circular cylinder barrel II 683 and the circular cylinder bottom II 686, which is also fixed by bolts.

[0033] like Figure 3 as well as Figures 6-11 As shown, the loading flange 612 and the test bearing housing 36 are fixed by bolts.

[0034] like Figure 3 as well as Figures 6-11As shown, the specific loading process of the torque load is as follows: First, the oil inlet pressure of the longitudinal loading hydraulic cylinder 67 is controlled to push out the piston assembly I 671. The piston assembly I 671 drives the spherical bearing seat 617 to move downward through the loading block I 672 (in this process, under the action of the lateral limiting block of the spherical bearing seat 617, the lateral loading seat 63, the lateral loading hydraulic cylinder 68 and the lateral displacement sensor 87 will also move downward along the longitudinal moving assembly 64 together), so that the loading force output by the longitudinal loading hydraulic cylinder 67 is transmitted to the loading shaft 611 through the spherical bearing 613. Since the loading shaft 611 is equivalent to a cantilever beam fixed to the test bearing seat 36, the force transmitted to the loading shaft 611 can be converted into a torque loaded on the test tapered roller bearing 35. The magnitude of the loading torque can be determined by the hydraulic pressure in the longitudinal loading hydraulic cylinder 67 and the specific dimensions of the torque loading device 6. The deflection angle of the outer ring of the test tapered roller bearing 35 can be determined by the reading of the longitudinal displacement sensor 86 and the specific dimensions of the torque loading device 6. Then, the oil inlet pressure of the lateral loading hydraulic cylinder 68 is controlled to push out the piston assembly II 681. The piston assembly II 681 drives the spherical bearing seat 617 forward through the loading block II 682 (in this process, under the action of the longitudinal limiting block of the spherical bearing seat 617, the longitudinal loading seat 62, the longitudinal loading hydraulic cylinder 67 and the longitudinal displacement sensor 86 will also move forward along the lateral moving assembly 65 together), so that the loading force output by the longitudinal loading hydraulic cylinder 67 is transmitted to the loading shaft 611 through the spherical bearing 613. Since the loading shaft 611 is equivalent to a cantilever beam fixed to the test bearing seat 36, the force transmitted to the loading shaft 611 can be converted into a torque loaded on the test tapered roller bearing 35. The magnitude of the loading torque can be determined by the hydraulic pressure in the lateral loading hydraulic cylinder 68 and the specific dimensions of the torque loading device 6. The deflection angle of the outer ring of the test tapered roller bearing 35 can be determined by the reading of the lateral displacement sensor 87 and the specific dimensions of the torque loading device 6. Finally, during the test, either longitudinal or lateral torque can be applied, or both longitudinal and lateral torque can be applied simultaneously.

[0035] like Figure 1 , Figure 3 , Figure 7 as well as Figure 12As shown, the test chamber 7 includes a front plate 71, a rear plate 72, a cover plate 73, a left side plate 74, a right side plate I 75, and a right side plate II 76. The front plate 71 is fixed to the base 1, cover plate 73, left side plate 74, right side plate I 75, and right side plate II 76 by bolts. The rear plate 72 is fixed to the base 1, cover plate 73, left side plate 74, right side plate I 75, and right side plate II 76 by bolts. The cover plate 73 is fixed to the square cylinder I 493 of the axial loading hydraulic cylinder 49 by bolts. The cover plate 73 is fixed to the square cylinder II 593 of the radial loading hydraulic cylinder 58 by bolts. The upper surface of the cover plate 73 has an annular groove for installing and positioning the cage roller assembly II 56. The cover plate 73 has a through hole concentric with the annular groove for installing and positioning the loading rod 51. The upper surface of the cover plate 73 contacts the sealing ring 55. The cover plate 73, the sealing ring 55, and the loading disc 54 form a sealed space, which provides a sealing effect for the cage roller assembly II 56. The left side plate 74 has a stepped hole in the center for installing the test bearing housing 33 and providing guidance for the axial movement of the test bearing housing 33; the left side plate 74 and the base 1 are fixed by bolts; the right side plate I 75 has two through holes for installing tie rod I 451 and tie rod II 461, and is fixed with tie rod I 451 and tie rod II 461 with clearance fit; the right side plate I 75 has a concave spherical surface for installing and positioning the outer spherical surface of the test bearing housing 36, and the concave spherical surface of the right side plate I 75 has a rectangular groove in the middle; the right side plate II 76 has two through holes for installing tie rod III 471 and tie rod IV 481, and is fixed with tie rod III 471 and tie rod IV 481 with clearance fit; the right side plate II 76 has a concave spherical surface for installing and positioning the outer spherical surface of the test bearing housing 36; the right side plate II 76 and the base 1 are fixed by bolts; the right side plate I 75, the right side plate II 76 and the test bearing housing 36 form a spherical bearing.

[0036] like Figures 3-12 As shown, the measurement system 8 includes pressure sensor I 81, pressure sensor II 82, pressure sensor III 83, pressure sensor IV 84, pressure sensor V 85, longitudinal displacement sensor 86, lateral displacement sensor 87, ultrasonic transmitter and receiver I 88, and ultrasonic transmitter and receiver II 89. Pressure sensors I81, II82, III83, IV84, and V85 are all annular hollow force sensors. The central hole of pressure sensor I81 is fixed to pull rod I451 with a clearance fit, and connected in series between right side plate I75 and nut I453. The central hole of pressure sensor II82 is fixed to pull rod II461 with a clearance fit, and connected in series between right side plate II76 and nut II463. The central hole of pressure sensor III83 is fixed to pull rod III471 with a clearance fit, and connected in series between right side plate II76 and nut III473. The central hole of pressure sensor IV84 is fixed to pull rod IV481 with a clearance fit, and connected in series between right side plate I75 and nut IV483. The central hole of pressure sensor V85 is fixed to loading rod 51 with a clearance fit, and connected in series between locking nut 52 and fixed disc 53. Both the longitudinal displacement sensor 86 and the lateral displacement sensor 87 are rod-type displacement sensors; the rod of the longitudinal displacement sensor 86 and the longitudinal limiting block of the spherical bearing housing 617 are fixed by threaded connection; the outer flange of the longitudinal displacement sensor 86 and the frame I 621 and frame II 622 of the longitudinal loading seat 62 are fixed by bolts; the rod of the lateral displacement sensor 87 and the lateral limiting block of the spherical bearing housing 617 are fixed by threaded connection; the outer flange of the lateral displacement sensor 87 and the frame III 631 and frame IV 632 of the lateral loading seat 63 are fixed by bolts. Ultrasonic transmitter and receiver I 88 and ultrasonic transmitter and receiver II 89 are used to measure the roller skew angle of the tested tapered roller bearing 35. The measurement principle is that two ultrasonic beams emitted by the transmitter are reflected from the roller surface of the tested tapered roller bearing 35 and return to the receiver. The skew angle of the roller is calculated based on the time difference between the round trip of the two ultrasonic beams and the roller rotation speed. Ultrasonic transmitter and receiver I 88 is used to emit ultrasonic signals to the small end surface of the roller of the tested tapered roller bearing 35 and to receive the ultrasonic signals reflected from the small end surface of the roller. Ultrasonic transmitter and receiver I 88 is installed in the groove of the tested bearing housing 36 and is threadedly connected to the tested bearing housing 36. Ultrasonic transmitter and receiver II 89 is used to emit ultrasonic signals to the large end surface of the roller of the tested tapered roller bearing 35 and to receive the ultrasonic signals reflected from the large end surface of the roller. Ultrasonic transmitter and receiver II 89 is installed in the groove of the tested bearing housing 36 and is threadedly connected to the tested bearing housing 36. Ultrasonic transmitter and receiver I 88 and ultrasonic transmitter and receiver II 89 are located in the same axial plane of the tested tapered roller bearing 35.

[0037] During the test, the servo motor 21 in the drive unit 2 is first started to drive the inner ring of the tested tapered roller bearing in the test shaft system 3 to rotate. Then, the measurement system 8 is turned on, and axial load, radial load, and torque load are applied to the tested tapered roller bearing respectively using the axial force loading device 4, radial force loading device 5, and torque loading device 6 as required. Under the action of the inner ring of the tested tapered roller bearing, the roller will rotate around its own axis and revolve around the bearing axis. The ultrasonic waves continuously emitted by the ultrasonic transmitter and receiver I 88 and the ultrasonic transmitter and receiver II 89 will pass through the outer ring of the tested tapered roller bearing and reach the inside of the bearing. When the small end or large end of the roller revolves to the outer raceway position (detection point) pointed to by the ultrasonic transmitter and receiver I 88 or the ultrasonic transmitter and receiver II 89, the emitted ultrasonic wave signal will be reflected by the surface of the small end or large end of the roller. The reflected ultrasonic wave signal will pass through the outer ring again and be received by the ultrasonic transmitter and receiver I 88 or the ultrasonic transmitter and receiver II 89. When the small or large end of the roller has not revolved to the outer raceway position (detection point) pointed to by ultrasonic transmitter receiver I88 or ultrasonic transmitter receiver II89, the reflected ultrasonic signal will be very weak due to the nonlinearity and discontinuity of the internal structure of the tested tapered roller bearing. Therefore, as all the rollers in the tested tapered roller bearing revolve, the signal received by ultrasonic transmitter receiver I88 or ultrasonic transmitter receiver II89 will exhibit a very obvious periodic characteristic. Based on this characteristic, the roller skew angle can be analyzed. The tapered roller skew angle can be calculated using formula (1).

[0038] (1) In the formula, It is the rolling element skew angle (rad); t s-end It is the moment (s) when the small end of the roller passes the detection point I88 of the ultrasonic transmitter and receiver; It is the time (s) for the ultrasonic wave to pass through the outer sheath at the detection point I88 of the ultrasonic transmitter and receiver; t l-end It is the time (s) when the large end of the roller passes the detection point II89 of the ultrasonic transmitter and receiver. R is the time (s) it takes for the ultrasonic wave to pass through the outer race at the ultrasonic transmitter / receiver II detection point 89; R is the radius (mm) of the outer race at the ultrasonic transmitter / receiver I detection point 88 or the ultrasonic transmitter / receiver II detection point 89. L is the revolution speed of the roller at the ultrasonic transmitter / receiver I detection point 88 or ultrasonic transmitter / receiver II detection point 89 (rad / s); L is the length of the raceway between the ultrasonic transmitter / receiver I detection point 88 and ultrasonic transmitter / receiver II detection point 89 (mm).

[0039] radius R and orbital speed Determined by formula (2): (2) In the formula, R s-end R is the radius (mm) of the outer raceway at the ultrasonic transmitter / receiver I88 detection point; l-end It is the radius (mm) of the outer raceway at the detection point II89 of the ultrasonic transmitter and receiver; The revolution speed of the roller at the ultrasonic transmitter and receiver I88 detection point (rad / s). The speed of the roller's revolution at the ultrasonic transmitter-receiver II89 detection point is rad / s.

[0040] The orbital speed of the roller at the ultrasonic transmitter and receiver I88 detection point Calculated using formula (3).

[0041] (3) In the formula, Z is the number of rollers; It is the time (s) when the previous roller passed the ultrasonic transmitter and receiver I88 detection point.

[0042] The orbital speed of the roller at the ultrasonic transmitter and receiver II89 detection point Calculated using formula (4).

[0043] (4) In the formula, Z is the number of rollers; It is the time (s) when the previous roller passed the detection point II89 of the ultrasonic transmitter and receiver.

[0044] This allows for the measurement and calculation of the roller skew angle of tapered roller bearings.

[0045] This invention enables non-destructive testing of the roller skew angle of tapered roller bearings under simulated radial force-axial force-torque combined load conditions. It provides an experimental platform for the fundamental theoretical research of tapered roller bearings, helps to evaluate the kinematic state of the rollers during service, and verifies the accuracy and rationality of the design parameters of tapered roller bearings.

[0046] The parts not described in detail in the above embodiments are existing technologies.

[0047] It should be noted that although the present invention has been described through the above embodiments, the present invention may have many other embodiments. Without departing from the spirit and scope of the present invention, those skilled in the art can obviously make various corresponding changes and modifications to the present invention, but all such changes and modifications should fall within the scope of protection of the appended claims and their equivalents.

Claims

1. A conical roller bearing roller skew angle testing rig, characterized by: It includes a base (1), and a drive device (2), a test shaft system (3), an axial force loading device (4), a radial force loading device (5), a torque loading device (6), a test chamber (7), and a measurement system (8) mounted on the base (1); The drive unit (2) is used to provide rotational torque to the test shaft system (3) and drive the test tapered roller bearing and the test tapered roller bearing in the test shaft system (3) to rotate; The test shaft system (3) is used to support and stabilize the test tapered roller bearing and the test tapered roller bearing. The drive device (2), axial force loading device (4), radial force loading device (5), torque loading device (6), and measuring system (8) are connected in series in the entire test bench. The test shaft system (3) is mounted on the base (1) via the test box (7). The axial force loading device (4) is used to provide axial force to the test tapered roller bearing and the test tapered roller bearing in the test shaft system (3); The radial force loading device (5) is used to provide radial force to the test tapered roller bearing and the test tapered roller bearing in the test shaft system (3); The torque loading device (6) is used to provide torque to the tested tapered roller bearing in the test shaft system (3); The test chamber (7) is used to support and stabilize the test shaft system (3), the axial force loading device (4) and the radial force loading device (5), while storing lubricating oil and reducing the influence of the external environment on the tested tapered roller bearing in the test shaft system (3); The measuring system (8) is used to detect the magnitude of the axial force provided by the axial force loading device (4), the magnitude of the radial force provided by the radial force loading device (5), the magnitude of the deflection angle of the outer ring of the tested tapered roller bearing, and the magnitude of the roller skew angle of the tested tapered roller bearing.

2. A saggering angle testing bench for a tapered roller bearing roller according to claim 1, characterized in that: The drive unit (2) includes a servo motor (21), a flange (22) and a base (23); the output shaft of the servo motor (21) and the flange (22) are connected by a flat key or spline, the servo motor (21) and the base (23) are fixed by bolts, and the base (23) and the base (1) are fixed by bolts.

3. A spherically seated taper roller bearing roller skew angle testing apparatus as set forth in claim 2, characterized in that: The test shaft system (3) includes a main shaft (31), a test tapered roller bearing (32), a test bearing housing (33), bushing I (34), a test tapered roller bearing (35), a test bearing housing (36), and bushing II (37); the main shaft (31) is a multi-stage stepped hollow shaft; the inner rings of the main shaft (31) and the test tapered roller bearing (32) are fixed with an interference fit; the outer ring of the test tapered roller bearing (32) and the test bearing housing (33) are fixed with an interference fit; the outer circular surface of the test bearing housing (33) is a stepped shaft with an annular groove on the end face; the main shaft (31) The test tapered roller bearing (32) is fixed with a clearance fit to the bushing I (34); the bushing I (34) is used to limit the axial position of the test tapered roller bearing (32) in the main shaft (31); the inner ring of the main shaft (31) and the test tapered roller bearing (35) is fixed with an interference fit; the outer ring of the test tapered roller bearing (35) and the test bearing housing (36) are fixed with an interference fit; the outer circular surface of the test bearing housing (36) is spherical; the main shaft (31) and bushing II (37) are fixed with a clearance fit; the bushing II (37) is used to limit the axial position of the test tapered roller bearing (35) in the main shaft (31); The flange (22) in the spindle (31) and drive unit (2) is fixed by bolts.

4. A spherically seated tapered roller bearing roller skew angle testing apparatus as set forth in claim 3, characterized in that: The axial force loading device (4) includes an annular loading disc (41), a cage roller assembly I (42), an elastic seal ring I (43), an elastic seal ring II (44), a tie rod assembly I (45), a tie rod assembly II (46), a tie rod assembly III (47), a tie rod assembly IV (48), and an axial loading hydraulic cylinder (49); one end face of the annular loading disc (41) has four grooves evenly distributed in the circumferential direction, the bottom surface of the groove is inclined in the circumferential direction, the bottom of the groove has an arc-shaped through hole, and the sides of the groove are all arc surfaces; the annular The other end face of the loading disc (41) has an annular groove, an inner flange and an outer flange, and the inner flange and the outer flange have sealing grooves; the cylindrical side of the annular loading disc (41) has an ear plate with a slot, the length direction of the slot being the radial direction of the annular loading disc (41); the sealing grooves of the two annular flanges of the annular loading disc (41) are used to install elastic sealing ring I (43) and elastic sealing ring II (44); elastic sealing ring I (43) and elastic sealing ring II (44) are used to seal the cage roller assembly I (42); The pull rod assembly I (45) includes pull rod I (451), pressure block I (452) and nut I (453); the pull rod I (451) and the arc-shaped through hole at the bottom of the groove of the annular loading disk (41) are fixed with clearance fit; the lower surface of the pressure block I (452) is a slope and contacts the bottom surface of the groove of the annular loading disk (41); the side surface of the pressure block I (452) is an arc and is fixed with clearance fit to the side surface of the groove of the annular loading disk (41); the upper surface of the pressure block I (451) is a plane and contacts the nut of the pull rod I (451); the pull rod I (451) and nut I (453) are fixed by threaded connection; The pull rod assembly II (46) includes pull rod II (461), pressure block II (462) and nut II (463); the pull rod II (461) and the arc-shaped through hole at the bottom of the groove of the annular loading disk (41) are fixed with clearance fit; the lower surface of the pressure block II (462) is a slope and contacts the bottom surface of the groove of the annular loading disk (41); the side surface of the pressure block II (462) is an arc and is fixed with clearance fit to the side surface of the groove of the annular loading disk (41); the upper surface of the pressure block II (461) is a plane and contacts the nut of the pull rod II (461); the pull rod II (461) and nut II (463) are fixed by threaded connection; The tie rod assembly Ⅲ (47) includes tie rod Ⅲ (471), pressure block Ⅲ (472) and nut Ⅲ (473); tie rod Ⅲ (471) and the arc-shaped through hole at the bottom of the groove of the annular loading disk (41) are fixed with clearance fit; the lower surface of pressure block Ⅲ (472) is inclined and contacts the bottom surface of the groove of the annular loading disk (41); the side surface of pressure block Ⅲ (472) is arc and is fixed with clearance fit to the side surface of the groove of the annular loading disk (41); the upper surface of pressure block Ⅲ (471) is flat and contacts the nut of tie rod Ⅲ (471); tie rod Ⅲ (471) and nut Ⅲ (473) are fixed by threaded connection; The pull rod assembly IV (48) includes pull rod IV (481), pressure block IV (482) and nut IV (483); the pull rod IV (481) and the arc-shaped through hole at the bottom of the groove of the annular loading disk (41) are fixed with clearance fit; the lower surface of the pressure block IV (482) is a slope and contacts the bottom surface of the groove of the annular loading disk (41); the side surface of the pressure block IV (482) is an arc and is fixed with clearance fit to the side surface of the groove of the annular loading disk (41); the upper surface of the pressure block I (481) is a plane and contacts the nut of the pull rod IV (481); the pull rod IV (481) and nut IV (483) are fixed by threaded connection; The parameters of tie rod assembly I (45), tie rod assembly II (46), tie rod assembly III (47) and tie rod assembly IV (48) are completely identical; The cage roller assembly I (42) includes a cage I (421), roller I (422), and flange I (423); the cage I (421) has four evenly distributed arc-shaped slots in the circumferential direction, and the four arc-shaped slots are respectively fixed with tie rod I (451), tie rod II (461), tie rod III (471), and tie rod IV (481) with clearance fit; several pockets are evenly distributed between two adjacent arc-shaped slots on the cage I (421), and the surface of the pockets in the circumferential direction of the cage I (421) is an arc surface; the cage I ( The pocket of cage I (421) is used to install and position roller I (422); the pocket of cage I (421) and roller I (422) are fixed with clearance fit; cage I (421) and flange I (423) are connected by rivets; flange I (423) is used to install and remove roller I (422) and to restrict the movement of roller I (422) in the radial direction of cage I (421); cage roller assembly I (42) is installed in the end face annular groove of the test bearing housing (33) and the end face annular groove of the annular loading disk (41); The axially loaded hydraulic cylinder (49) is a structure symmetrical about the central cross section, including piston rod I (491), piston I (492), square cylinder I (493), square cylinder head I (494) and square cylinder head II (495); the piston rod I (491) and the ear plate of the annular loading disk (41) are fixed with a clearance fit; the piston rod I (491) and piston I (492) are fixed by bolts; the square cylinder I (493) is rectangular; a soft seal is used between the square cylinder I (493) and piston I (492); a soft seal is used between the square cylinder I (493) and square cylinder head I (494) and square cylinder head II (495), and they are fixed by bolts; the square cylinder head I (494) and square cylinder head II (495) are equipped with oil ports.

5. A spherically seated tapered roller bearing roller skew angle testing apparatus as set forth in claim 4, characterized in that: The radial force loading device (5) includes a loading rod (51), a locking nut (52), a fixed disc (53), a loading disc (54), a sealing ring (55), a cage roller assembly II (56), a loading bearing housing (57), and a radial loading hydraulic cylinder (58); the loading rod (51) and the locking nut (52) are fixed by a threaded connection; the loading rod (51) and the fixed disc (53) are fixed by a key connection; the lower surface of the fixed disc (53) has several fan-shaped surfaces, which are planar in the radial direction and inclined in the circumferential direction; the loading... The rod (51) and the loading disk (54) are fixed with a clearance fit; the upper surface of the loading disk (54) has several fan-shaped surfaces, which are flat in the radial direction and inclined in the circumferential direction; the cylindrical side of the loading disk (54) has L-shaped ear plates with tapered through holes; the lower surface of the loading disk (54) has an annular groove and an annular flange, and the annular flange has a sealing groove; the annular groove of the loading disk (54) is used to install and position the cage roller assembly II (56); the sealing groove of the loading disk (54) is used to install the sealing ring (55). The cage roller assembly II (56) includes a cage II (561), roller II (562) and flange II (563); the cage (561) has a circular through hole in the center, and the circular through hole and the loading rod (51) are fixed with clearance fit; the cage II (561) has a number of pockets evenly distributed in the circumferential direction, and the surface of the pockets in the circumferential direction of the cage II (561) is an arc surface; The pocket of cage II (561) and roller II (562) are fixed with clearance fit; The cage II (561) and the flange II (563) are connected by rivets; the flange II (563) is used to install and remove the roller II (562) and to restrict the movement of the roller II (562) in the radial direction of the cage II (561); The loading bearing housing (57) includes cylindrical roller bearing I (571), cylindrical roller bearing II (572), cylindrical bearing housing (573), retaining ring I (574), and retaining ring II (575); cylindrical roller bearing I (571) is a cylindrical roller bearing with no inner ring flange or no outer ring flange, its inner ring is fixed to the main shaft (31) with an interference fit, and its outer ring is fixed to the cylindrical bearing housing (573) with an interference fit; cylindrical roller bearing II (572) is a cylindrical roller bearing with no inner ring flange or no outer ring flange, its inner ring is fixed to the main shaft (31) with an interference fit, and its outer ring is fixed to the cylindrical bearing housing (573) with an interference fit; the cylindrical bearing housing (573) is rectangular in shape, and its upper surface is connected to the loading rod (51). The cylindrical bearing housing (573) is fixed with bolts; each of the four corners of the cylindrical bearing housing (573) has a through hole, and the four through holes are respectively fixed with tie rod I (451), tie rod II (461), tie rod III (471), and tie rod IV (481) with clearance fit; retaining ring I (574) is used to limit the axial movement of the outer ring of cylindrical roller bearing I (571) and is fixed with the cylindrical bearing housing (573) by bolts; retaining ring II (575) is used to limit the axial movement of the outer ring of cylindrical roller bearing II (572) and is fixed with the cylindrical bearing housing (573) by bolts; bushing I (34) is used to limit the axial movement of the inner ring of cylindrical roller bearing I (571); bushing II (37) is used to limit the axial movement of the inner ring of cylindrical roller bearing II (572); The radial loading hydraulic cylinder (58) is a structure symmetrical about the central cross section, including piston rod II (581), piston II (582), square cylinder barrel II (583), square cylinder head III (584) and square cylinder head IV (585); the piston rod II (581) and the loading disc (54) ear plate are fixed by a tapered through hole clearance fit; Piston rod II (581) and piston II (582) are fixed by bolts; the square cylinder II (583) is rectangular in shape and is soft-sealed with piston II (582); the square cylinder II (583) is soft-sealed with square cylinder head III (584) and square cylinder head IV (585) respectively, and is fixed by bolts; the square cylinder head III (584) and square cylinder head IV (585) are equipped with oil ports.

6. A spherically seated tapered roller bearing roller skew angle testing apparatus as set forth in claim 5, characterized in that: The torque loading device (6) includes a loading shaft assembly (61), a longitudinal loading seat (62), a transverse loading seat (63), a longitudinal moving assembly (64), a transverse moving assembly (65), a support assembly (66), a longitudinal loading hydraulic cylinder (67), and a transverse loading hydraulic cylinder (68). The loading shaft assembly (61) includes a loading shaft (611), a loading flange (612), a spherical plain bearing (613), an inner retaining ring (614), an outer retaining ring I (615), an outer retaining ring II (616), and a spherical plain bearing housing (617); the loading shaft (611) and the loading flange (612) are connected by a spline; the loading flange (612) and the bearing housing under test (36) are fixed by bolts; the loading shaft (611) and the inner ring of the spherical plain bearing (613) are fixed by an interference fit; the loading shaft (611) and the inner retaining ring (614) are connected by... Bolt fixing; inner ring retainer (614) is used to limit the axial movement of the inner ring of the spherical plain bearing (613); the outer ring of the spherical plain bearing (613) and the spherical plain bearing housing (617) are fixed by interference fit; outer ring retainer I (615) and outer ring retainer II (616) are fixed to the spherical plain bearing housing (617) by bolts respectively; outer ring retainer I (615) and outer ring retainer II (616) are used to limit the axial movement of the outer ring of the spherical plain bearing (613); the spherical plain bearing housing (617) has a cross-shaped structure and has protruding limiting blocks in the longitudinal and transverse directions respectively; The longitudinal loading seat (62) includes frame I (621) and frame II (622); the structures of frame I (621) and frame II (622) are the same and are fixed by bolts; the longitudinal loading seat (62) composed of frame I (621) and frame II (622) and the longitudinal limiting block of the spherical bearing seat (617) are fixed by clearance fit; The transverse loading seat (63) includes frame III (631) and frame IV (632); frame III (631) and frame IV (632) have the same structure and are fixed by bolts; the transverse loading seat (63) composed of frame III (631) and frame IV (632) and the transverse limiting block of the spherical bearing seat (617) are fixed with clearance fit; the longitudinal loading seat (62) passes through the transverse loading seat (63) and is fixed with clearance fit to the transverse loading seat (63); The longitudinal movement assembly (64) includes slider group I (641), guide rail group I (642), stop group I (643), slider group II (644), guide rail group II (645), and stop group II (646); the outer side of frame III (631) is fixed to slider group I (641) by bolts, and slides on guide rail group I (642) through slider group I (641); stop group I (643) is used to limit the limit displacement of slider group I (641); the outer side of frame IV (632) is fixed to slider group II (644) by bolts, and slides on guide rail group II (645) through slider group II (644); stop group II (646) is used to limit the limit displacement of slider group II (644); The lateral movement assembly (65) includes slider group III (651), guide rail group III (652), stop group III (653), slider group IV (654), guide rail group IV (655), and stop group IV (656); the outer side of frame I (621) is fixed to slider group III (651) by bolts, and slides on guide rail group III (652) through slider group III (651); stop group III (653) is used to limit the ultimate displacement of slider group III (651); the outer side of frame II (622) is fixed to slider group IV (654) by bolts, and slides on guide rail group IV (655) through slider group IV (654); stop group IV (656) is used to limit the ultimate displacement of slider group IV (654); The bracket assembly (66) includes a front bracket (661), a column assembly (662), and a rear bracket (663); the front bracket (661) and the base (1) are fixed by bolts; the front bracket (661) is connected to the rear bracket (663) via the column assembly (662), and the front bracket (661), column assembly (662), and rear bracket (663) are fixed by bolts; the rear bracket (663) and the base (1) are fixed by bolts; the front bracket (661) and guide rail assembly I (642) are fixed by bolts; the front bracket ( 661) and stop block group I (643) are fixed by bolts; front bracket (661) and guide rail group III (652) are fixed by bolts; front bracket (661) and stop block group III (653) are fixed by bolts; rear bracket (663) and guide rail group II (645) are fixed by bolts; rear bracket (663) and stop block group II (646) are fixed by bolts; rear bracket (663) and guide rail group IV (655) are fixed by bolts; rear bracket (663) and stop block group IV (656) are fixed by bolts; The longitudinal loading hydraulic cylinder (67) includes piston assembly I (671), loading block I (672), circular cylinder barrel I (673), circular cylinder head I (674), guide sleeve I (675), and circular cylinder bottom I (676); the piston rod of piston assembly I (671) and loading block I (672) are fixed by bolts; loading block I (672) and spherical bearing seat (617) are fixed by bolts; there is a soft seal between the piston of piston assembly I (671) and circular cylinder barrel I (673); there is a soft seal between circular cylinder barrel I (673) and circular cylinder head I (674); the frame I (621) and frame II (622) of circular cylinder barrel I (673), circular cylinder head I (674), and longitudinal loading seat (62) are fixed by bolts; there is a soft seal between circular cylinder barrel I (673) and circular cylinder bottom I (676), and they are fixed by bolts. The transverse loading hydraulic cylinder (68) includes piston assembly II (681), loading block II (682), circular cylinder barrel II (683), circular cylinder head II (684), guide sleeve II (685), and circular cylinder bottom II (686); the piston rod of piston assembly II (681) and loading block II (682) are fixed by bolts; loading block II (682) and spherical bearing seat (617) are fixed by bolts; there is a soft seal between the piston of piston assembly II (681) and circular cylinder barrel II (683); there is a soft seal between circular cylinder barrel II (683) and circular cylinder head II (684); the frame III (631) and frame IV (632) of circular cylinder barrel II (683), circular cylinder head II (684), and transverse loading seat (63) are fixed by bolts; there is a soft seal between circular cylinder barrel II (683) and circular cylinder bottom II (686), and they are fixed by bolts.

7. A spherically seated taper roller bearing roller skew angle testing apparatus as set forth in claim 6, characterized in that: The test chamber (7) includes a front plate (71), a rear plate (72), a cover plate (73), a left side plate (74), a right side plate I (75), and a right side plate II (76); the front plate (71) is fixed to the base (1), the cover plate (73), the left side plate (74), the right side plate I (75), and the right side plate II (76) by bolts; the rear plate (72) is fixed to the base (1), the cover plate (73), the left side plate (74), the right side plate I (75), and the right side plate II (76) by bolts; the cover plate (73) is fixed to the axial loading hydraulic cylinder (49) by bolts. The square cylinder I (493) is fixed by bolts; the square cylinder II (593) of the cover plate (73) and the radial loading hydraulic cylinder (58) is fixed by bolts; the upper surface of the cover plate (73) has an annular groove for installing and positioning the cage roller assembly II (56); the cover plate (73) has a through hole concentric with the annular groove for installing and positioning the loading rod (51); the upper surface of the cover plate (73) contacts the sealing ring (55); the cover plate (73), the sealing ring (55) and the loading disc (54) form a sealed space for the cage roller assembly Part II (56) serves as a seal; the center of the left side plate (74) has a stepped hole for installing the test bearing housing (33) and for guiding the axial movement of the test bearing housing (33); the left side plate (74) and the base (1) are fixed by bolts; the right side plate I (75) has two through holes for installing tie rod I (451) and tie rod II (461), and is fixed with tie rod I (451) and tie rod II (461) with clearance fit; the right side plate I (75) has a concave spherical surface for installing and positioning the test bearing housing (36). The outer spherical surface of the right side plate I (75) has a rectangular groove in the middle of the concave spherical surface; the right side plate II (76) has two through holes for installing tie rod III (471) and tie rod IV (481), and is fixed with tie rod III (471) and tie rod IV (481) with clearance fit; the right side plate II (76) has a concave spherical surface for installing and positioning the outer spherical surface of the test bearing seat (36); the right side plate II (76) and the base (1) are fixed by bolts; the right side plate I (75), the right side plate II (76) and the test bearing seat (36) form a spherical bearing.

8. The test bench for detecting the skew angle of tapered roller bearings according to claim 1, characterized in that: The measurement system (8) includes pressure sensor I (81), pressure sensor II (82), pressure sensor III (83), pressure sensor IV (84), pressure sensor V (85), longitudinal displacement sensor (86), lateral displacement sensor (87), ultrasonic transmitter and receiver I (88) and ultrasonic transmitter and receiver II (89). Pressure sensor I (81), pressure sensor II (82), pressure sensor III (83), pressure sensor IV (84), and pressure sensor V (85) are all annular hollow force sensors; the center hole of pressure sensor I (81) is fixed with a clearance fit to pull rod I (451) and connected in series between right side plate I (75) and nut I (453); the center hole of pressure sensor II (82) is fixed with a clearance fit to pull rod II (461) and connected in series between right side plate II (76) and nut II (453). Between 63); the center hole of pressure sensor III (83) and pull rod III (471) are fixed with clearance fit, and connected in series between right side plate II (76) and nut III (473); the center hole of pressure sensor IV (84) and pull rod IV (481) are fixed with clearance fit, and connected in series between right side plate I (75) and nut IV (483); the center hole of pressure sensor V (85) and loading rod (51) are fixed with clearance fit, and connected in series between locking nut (52) and fixed disc (53); Both the longitudinal displacement sensor (86) and the transverse displacement sensor (87) are rod-type displacement sensors; the rod of the longitudinal displacement sensor (86) and the longitudinal limiting block of the spherical bearing seat (617) are fixed by threaded connection; the outer flange of the longitudinal displacement sensor (86) and the frame I (621) and frame II (622) of the longitudinal loading seat (62) are fixed by bolts; the rod of the transverse displacement sensor (87) and the transverse limiting block of the spherical bearing seat (617) are fixed by threaded connection; the outer flange of the transverse displacement sensor (87) and the frame III (631) and frame IV (632) of the transverse loading seat (63) are fixed by bolts; Ultrasonic transmitter-receiver I (88) and ultrasonic transmitter-receiver II (89) are used to measure the roller skew angle of the tested tapered roller bearing (35). The measurement principle is that two ultrasonic beams emitted by the transmitter are reflected from the roller surface of the tested tapered roller bearing (35) and return to the receiver. The roller skew angle is calculated based on the time difference between the round trip of the two ultrasonic beams and the roller rotation speed. Ultrasonic transmitter-receiver I (88) is used to emit ultrasonic signals to the small end surface of the roller of the tested tapered roller bearing (35) and receive ultrasonic signals reflected from the small end surface of the roller. (88) is installed in the groove of the bearing housing (36) under test and is connected to the bearing housing (36) under test by threads; ultrasonic transmitter receiver II (89) is used to transmit ultrasonic signals to the large end surface of the roller of the tapered roller bearing (35) under test and to receive ultrasonic signals reflected from the large end surface of the roller; ultrasonic transmitter receiver II (89) is installed in the groove of the bearing housing (36) under test and is connected to the bearing housing (36) under test by threads; ultrasonic transmitter receiver I (88) and ultrasonic transmitter receiver II (89) are located in the same axial plane of the tapered roller bearing (35) under test.

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