A crank-rocker type end face friction and wear testing machine

Abstract

This invention discloses a crank-rocker type end-face friction and wear testing machine, belonging to the field of end-face friction and wear testing technology. It includes a frame, a load-equalizing system, a crank-rocker testing system, and a transmission system, all mounted on the frame, which provides support for each system. The invention uses the load-equalizing system to adjust the contact pressure of the end-face friction and wear specimen and ensure the uniformity of load application at both ends, simulating the end-face friction and wear phenomenon of the specimen under real heavy-load conditions. The crank-rocker testing system simulates end-face oscillating friction and wear or intermittent end-face circumferential friction and wear. The transmission system drives the crank-rocker testing system or applies the load to the load-equalizing system. This invention has advantages such as adjustable end-face contact pressure, uniform load application at both ends, ability to simulate oscillating friction and wear or intermittent end-face circumferential friction and wear, ability to simulate end-face friction and wear of two specimens in a single experiment, and simple structure.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of end face friction and wear experiment, and particularly relates to a crank rocker type end face friction and wear experiment machine which can simulate and realize experimental research on reciprocating swing or intermittent rotation end face friction and wear under different load and rotation speed conditions. BACKGROUND

[0002] In the current situation of continuous and rapid development in the field of engineering technology, the performance requirements of various engineering materials are becoming increasingly stringent, and the reciprocating swing or intermittent rotation end face friction and wear performance is particularly concerned. Today, engineering materials not only need to withstand increasing load, but also are widely used in various application scenarios. In terms of evaluating the reciprocating swing or intermittent rotation end face friction and wear performance of engineering materials, the end face friction and wear experiment machine is an important test equipment. The traditional end face friction and wear experiment machine usually adopts two samples to rotate at a high speed under specific experimental conditions, and explores the end face friction and wear performance of the materials by different rotation speed ratios and pressure. Although this simulation method can reflect the end face friction and wear characteristics of the materials to some extent, it still has significant differences with the real reciprocating swing or intermittent rotation end face friction and wear working conditions, and cannot completely and accurately simulate the complex situations in actual operation.

[0003] With the continuous progress of science and technology, the limitations of the existing end face friction and wear experiment method in simulating real working conditions have become increasingly prominent, and the demand for improvement and innovation has become extremely urgent. If the contact and grinding mode of the standard upper sample and lower sample in the traditional end face friction and wear experiment machine is changed to reciprocating swing or intermittent rotation working conditions, the tribological performance of the materials in the actual reciprocating swing or intermittent rotation end face friction and wear process can be more accurately reflected. Therefore, a scheme is proposed to change the contact and grinding mode of the standard upper sample and lower sample in the traditional end face friction and wear experiment machine to reciprocating swing or intermittent rotation contact working conditions by using a crank rocker mechanism, aiming to provide a more effective test means for the accurate evaluation of the end face friction and wear performance of engineering materials under specific working conditions.

[0004] Patent CN112067487A discloses a kind of end face friction and wear testing machine and its test method, its features are as follows: a kind of end face friction and wear testing machine and its test method, including rack assembly, test assembly and load loading assembly, test assembly includes first driving device, main shaft, fixture base, first driving device is fixed on rack assembly and is transmission connection with main shaft, main shaft is rotated around its own axis and is fixed on rack assembly, and main shaft bottom is fixed with upper sample, lower sample is fixed in the inside of fixture base upper end, upper sample is rotated relative to lower sample and constitutes friction pair, one end of steel wire rope connected fixed on the outside surface of fixture base, the other end of steel wire rope is connected with cantilever load cell fixed on rack assembly, cantilever load cell is connected with computer.The application can be adjusted and selected in a wide range by load, speed, time, temperature and friction pair coupling material, finish, hardness and other parameters, the change of friction and wear performance of test material under the action of various influencing factors is investigated, and the tribological characteristics and comprehensive use performance of sample material under dry friction condition are evaluated according to the change of test parameters and the wear condition of sample surface under different conditions, especially suitable for evaluating the friction and wear reduction characteristics and comprehensive use performance of self-lubricating bearing material, surface thin layer or layered composite material, solid lubricating material, but it cannot simulate real reciprocating swing or intermittent rotation working condition, it is difficult to ensure the high accuracy of experimental results.

[0005] Patent CN101832898A discloses a kind of horizontal end face friction and wear testing machine, its features are as follows: a kind of horizontal end face friction and wear testing machine, the testing machine is mainly composed of power system, transmission system, axial force loading system, torsional load loading system, test system and auxiliary support system.In actual use, it can be adjusted and selected in a wide range by load, speed, time, temperature and friction pair surface condition parameters, both the change of friction and wear performance of small product sample under the action of various influencing factors can be investigated, and the corresponding physical parts can also be simulated for actual use condition test research, so as to realize the comprehensive investigation and analysis of tribological characteristics of sample material and corresponding product use performance.But the experimental stress that device itself can load is limited, and there is still a certain gap between simulated working condition and actual working condition.

[0006] The equal load system is used to simulate heavy load end face contact working condition, has the advantages of large load adjustment range, large torque transmission, smooth and symmetrical load application, high control accuracy, etc., the crank rocker experimental system is used to simulate reciprocating swing or intermittent rotation end face friction and wear, has the advantages of adjustable reciprocating swing angle, adjustable intermittent rotation angle, etc., the transmission system is used to realize gear shifting adjustment of the crank rocker experimental system driving and the equal load system loading, the experimental device can simulate end face friction and wear of two samples at a time, greatly shortens the experimental time, and the crank rocker type end face friction and wear experimental machine is provided, and experimental scheme and experimental reference are provided for simulating real reciprocating swing or intermittent rotation end face friction and wear. SUMMARY

[0007] The crank rocker type end face friction and wear experimental machine provided by the application can simulate heavy load end face contact working condition through the equal load system, simulate reciprocating swing or intermittent rotation end face friction and wear through the crank rocker experimental system, realize gear shifting adjustment through the transmission system, and provide a new experimental scheme for simulating real reciprocating swing or intermittent rotation end face friction and wear, improve the accuracy and reliability of experimental results, and improve the experimental efficiency.

[0008] In order to achieve the above-mentioned purpose, the application provides the following technical scheme:

[0009] A crank rocker type end face friction and wear experimental machine, comprising a rack, an equal load system, a crank rocker experimental system and a transmission system, each system is installed on the rack, and the rack provides installation support for each system;

[0010] The equal load system is used to realize adjustment of end face friction and wear sample contact pressure and uniformity of two-end load application.

[0011] The crank rocker experimental system is used to switchably simulate reciprocating swing type end face friction and wear or intermittent type end face circumferential friction and wear, and end face friction and wear of two samples can be simulated at a time.

[0012] The transmission system is used to provide power for load application of the equal load system or movement driving of the crank rocker experimental system through gear shifting.

[0013] As a further technical scheme of the application, the equal load system comprises a loading head, an equal load spring, a joint bearing assembly, a loading shaft, an equal load adjusting assembly and a joint bearing loading weight.

[0014] The loading head is provided with a spring hanging rack, and the two ends of the equal load spring are respectively hung on the spring hanging racks of the two loading heads arranged symmetrically.

[0015] One end of the loading shaft is connected with the loading head, and the other end is connected with the uniform loading nut connecting block, the uniform loading bolt and the uniform loading adjusting assembly through the loading shaft;

[0016] The joint bearing assembly comprises a joint bearing inner ring, a joint bearing outer ring and a joint bearing dovetail pin, the shaft end of the loading shaft passes through the joint bearing inner ring, the joint bearing inner ring is matched with the joint bearing outer ring, the bottom of the joint bearing outer ring is fixedly connected with the joint bearing dovetail pin, and the side surface is fixedly connected with the joint bearing loading weight;

[0017] The uniform loading adjusting assembly comprises a uniform loading nut, a uniform loading double-headed screw rod, a turbine and a worm, the uniform loading nut is matched with the uniform loading double-headed screw rod, the turbine is installed in the middle segment of the uniform loading double-headed screw rod and is connected through a key, the worm is matched with the turbine, and the uniform loading nut is fixed with the loading shaft and the uniform loading nut connecting block through the uniform loading bolt.

[0018] As a further technical scheme of the present application, the middle segment of the uniform loading double-headed screw rod is symmetrically installed with uniform loading double-headed screw rod bearings on both sides, the optical axis segment of the worm is installed with a worm bearing, and the joint bearing dovetail pin is slidably connected with the joint bearing guide rail on the rack.

[0019] As a further technical scheme of the present application, the crank rocker experimental system comprises an experimental shaft, a sample clamping assembly, a crank assembly, a connecting rod, a rocker and a working condition switching assembly.

[0020] The sample clamping assembly comprises annular auxiliary test pieces symmetrically installed at both ends of the experimental shaft and a sample box for fixing a gasket sample, the annular auxiliary test pieces are in surface-to-surface contact with the end surfaces of the gasket sample to form a friction pair, and the bottom of the sample box is connected with the joint bearing loading weight of the uniform loading system.

[0021] The crank assembly comprises a crank driving shaft, a crank length adjusting slider, a crank length adjusting slider bolt and a crank length adjusting slider bolt nut, the crank length adjusting slider is slidably matched with the crank main body through a crank length adjusting slider slot, and the crank length adjusting slider bolt and the crank length adjusting slider bolt nut are used to lock the position of the crank length adjusting slider.

[0022] One end of the connecting rod is hingedly connected with the crank length adjusting slider through a crank screw rod and a crank nut, and the other end is hingedly connected with one end of the rocker through a rocker screw rod and a rocker nut.

[0023] The working condition switching assembly comprises a sliding spline, a ratchet, a pawl and a pawl slider, the experimental shaft is provided with an experimental shaft outer spline shaft segment and a ratchet sliding shaft segment, the sliding spline is matched with the experimental shaft outer spline shaft segment, the ratchet is matched with the ratchet sliding shaft segment through a ratchet sliding key, the pawl is installed on the pawl slider through a pawl bolt, the pawl slider is installed in a pawl slider sliding groove of the rocker, and the pawl and the ratchet can selectively form a ratchet and pawl matching.

[0024] As a further technical scheme of the application, the experimental shaft is provided with a rocker and an experimental shaft idling shaft segment, the rocker is provided with a rocker and experimental shaft idling hole segment and a rocker and experimental shaft idling positioning stepped hole segment matched with the idling shaft segment, and the rocker and experimental shaft idling positioning stepped hole segment is matched with a rocker and experimental shaft idling positioning stepped shaft segment on the experimental shaft to limit the axial degree of freedom of the rocker.

[0025] The rocker is provided with a rocker inner spline hole segment, when the working condition is switched to reciprocating swing, the sliding spline is slid to be matched with the rocker inner spline hole segment, and the experimental shaft is driven to reciprocate; when the working condition is switched to intermittent circumferential condition, the ratchet is slid to be matched with the pawl, and the experimental shaft is driven to rotate intermittently through the ratchet and pawl mechanism.

[0026] As a further technical scheme of the application, the annular test piece is provided with an annular test piece clamping groove and an annular test piece mounting shaft, the experimental shaft is provided with an annular test piece mounting hole and an annular test piece clamping bolt, the annular test piece mounting shaft is inserted into the annular test piece mounting hole, and the annular test piece clamping groove is clamped and fixed with the annular test piece clamping bolt; the top of the sample box is provided with an installation hole with internal threads, a gasket sample is pressed and fixed in the installation hole through a sample pressing nut, and the side surface of the sample box is provided with a torque sensor connector.

[0027] As a further technical scheme of the application, the transmission system comprises a motor, a gear shifting spline, a spline hole and light hole integrated shaft, and a gear transmission assembly.

[0028] The output shaft of the motor is provided with an output gear, and the gear transmission assembly comprises an intermediate drive spur gear, an intermediate drive bevel gear, a drive bevel gear, a drive spur gear and a crank spur gear.

[0029] The intermediate drive spur gear is engaged with the output gear, the center of the intermediate drive spur gear is provided with an intermediate drive spur gear spline hole, the gear shifting spline passes through the intermediate drive spur gear spline hole and is matched with the spline hole and light hole integrated shaft, the inner cavity of the spline hole and light hole integrated shaft is provided with a spline hole segment and a light hole segment, the gear shifting spline can be slid to be matched with the spline hole segment to drive the spline hole and light hole integrated shaft to rotate, or the gear shifting spline can be idle in the light hole segment.

[0030] The spline hole light hole integrated shaft is connected with an intermediate drive bevel gear at one end, the intermediate drive bevel gear is engaged at a 90° angle with a drive bevel gear, the drive bevel gear is connected with a drive spur gear through a drive shaft, and the drive spur gear is engaged with a crank spur gear installed on a crank drive shaft.

[0031] The spline hole light hole integrated shaft is connected with an intermediate drive bevel gear at one end, the intermediate drive bevel gear is engaged at a 90° angle with a drive bevel gear, the drive bevel gear is connected with a drive spur gear through a drive shaft, and the drive spur gear is engaged with a crank spur gear installed on a crank drive shaft.

[0032] As a further technical solution of the present application: the output shaft of the motor is provided with an output gear bearing, the drive shaft is provided with a drive gear bearing, the loading input gear is provided with a loading input end bearing, the intermediate drive spur gear is provided with an intermediate drive gear bearing, the worm is provided with a loading output end bearing, and the crank drive shaft is provided with a crank bearing two, and the outer rings of the bearings are all mounted on the rack through corresponding bearing supports.

[0033] As a further technical solution of the present application: the rack includes a bottom plate and joint bearing guide rail supports, experimental shaft bearing supports, crank bearing supports, motor supports, uniform load nut supports, uniform load double-end screw bearing supports, worm bearing supports, uniform load gear bearing supports and intermediate drive gear bearing supports installed on the bottom plate, and each support provides mounting support for the corresponding components.

[0034] As a further technical solution of the present application: the pawl sliding block is slidably connected with the rocker through a pawl sliding block sliding groove, the pawl is hingedly connected with the pawl sliding block through a pawl bolt, and the pawl sliding block is provided with a pawl sliding block bolt and a pawl sliding block bolt nut for locking the position of the pawl sliding block.

[0035] The present application provides a crank rocker type end face friction and wear test machine, which has the following advantages and beneficial effects:

[0036] The present application adopts a uniform load system to simulate heavy load end face contact conditions, has the advantages of large load adjustment range, large torque transmission, stable and symmetrical load application, high control precision, etc., and adopts a crank rocker test system to simulate reciprocating swing or intermittent rotation end face friction and wear, simulate the service performance of real end face contact under reciprocating swing or intermittent rotation conditions, has the advantages of adjustable reciprocating swing angle, adjustable intermittent rotation angle, etc., adopts a transmission system to realize gear shifting adjustment of the crank rocker test system driving and the uniform load system loading, the experimental device can simulate end face friction and wear of two samples at a time, greatly shortens the experimental time, provides an experimental scheme and experimental reference for simulating real reciprocating swing or intermittent rotation end face friction and wear, and has good use value and application prospect. BRIEF DESCRIPTION OF DRAWINGS

[0037] Figure 1Front isometric view of the overall structure of a crank rocker type end face friction and wear testing machine according to the present application;

[0038] Figure 2 Back isometric view of the overall structure of a crank rocker type end face friction and wear testing machine according to the present application;

[0039] Figure 3 Structure schematic diagram of the load sharing system according to the present application;

[0040] Figure 4 Structure schematic diagram of the knuckle bearing assembly according to the present application;

[0041] Figure 5 Structure schematic diagram of the worm gear load sharing assembly according to the present application;

[0042] Figure 6 Structure schematic diagram of the crank rocker testing system according to the present application;

[0043] Figure 7 Structure schematic diagram of the crank assembly according to the present application;

[0044] Figure 8 Structure schematic diagram of the rocker assembly according to the present application;

[0045] Figure 9 Structure schematic diagram of the testing shaft assembly according to the present application;

[0046] Figure 10 Structure schematic diagram of the sample clamping assembly according to the present application;

[0047] Figure 11 Structure schematic diagram of the transmission system according to the present application;

[0048] Figure 12 Structure schematic diagram of the gear shifting assembly according to the present application;

[0049] Figure 13 Structure schematic diagram of the spline hole and light hole integrated shaft according to the present application.

[0050] Wherein: 1-bottom plate; 2-knuckle bearing guide rail support; 3-knuckle bearing guide rail; 4-test shaft bearing support; 5-load sharing system; 51-loading head; 52-load sharing hanging spring; 53-knuckle bearing outer ring; 54-knuckle bearing inner ring; 55-knuckle bearing dovetail pin; 56-knuckle bearing loading weight; 57-loading shaft; 58-loading shaft and load sharing nut connecting block; 59-load sharing bolt; 510-load sharing nut; 511-worm bearing; 512-worm; 513-turbine; 514-load sharing double-headed screw bearing; 515-load sharing double-headed screw; 6-crank rocker test system; 61-sample box; 62-torque sensor joint; 63-test shaft bearing; 64-ring-shaped test piece; 65-gasket sample; 66-sample compression nut; 67-crank bearing one; 68-crank drive shaft; 69-crank nut; 610-connecting rod; 611-crank screw; 612-crank length adjustment sliding block; 613-crank length adjustment sliding block bolt; 614-crank length adjustment sliding block bolt nut; 615-crank length adjustment sliding block sliding groove; 616-crank hole; 617-rocker nut; 618-rocker screw; 619-rocker; 620-pawl sliding block bolt; 621-ratchet wheel; 622-pawl; 623-pawl bolt; 624-pawl sliding block sliding groove; 625-pawl sliding block; 626-pawl sliding block bolt nut; 627-ring-shaped test piece clamping groove; 628-ring-shaped test piece mounting shaft; 629-ring-shaped test piece mounting hole; 630-ring-shaped test piece clamping bolt; 631-test shaft outer spline shaft segment; 632-sliding spline; 633-rocker and test shaft idling shaft segment; 634-ratchet wheel sliding shaft segment; 635-rocker inner spline hole segment; 636-rocker and test shaft idling hole segment; 637-rocker and test shaft idling positioning step hole segment; 638-ratchet wheel limiting stopper; 639-ratchet wheel sliding key; 640-rocker and test shaft idling positioning step shaft segment; 641-sliding spline limiting stopper; 7-crank bearing support; 8-transmission system; 81-loading output end bearing; 82-loading output end bearing support; 83-loading output end gear; 84-loading input end gear; 85-loading input end bearing; 86-gear shifting spline; 87-motor; 88-output gear bearing; 89-intermediate drive spur gear; 810-intermediate drive gear bearing; 811-intermediate drive bevel gear; 812-driving bevel gear; 813-crank bearing two; 814-crank spur gear; 815-driving spur gear; 816-driving gear bearing; 817-driving shaft; 818-output gear; 819-spline hole and light hole integrated shaft; 820-intermediate drive spur gear spline hole; 9-driving gear bearing support; 10-output gear bearing support; 11-motor support; 12-load sharing nut support; 13-load sharing double-headed screw bearing support; 14-worm bearing support; 15-load sharing gear bearing support; 16-intermediate drive gear bearing support. DETAILED DESCRIPTION

[0051] The present invention will be further described below with reference to the embodiments. It should be noted that these are merely examples and descriptions of the inventive concept. Those skilled in the art can make various modifications or additions to the specific embodiments described or use similar methods to replace them, as long as they do not deviate from the inventive concept or exceed the scope defined in the claims, they should all be considered to fall within the protection scope of the present invention.

[0052] See Figure 1 , Figure 2 This invention relates to a crank-rocker type end face friction and wear testing machine, which is mainly composed of a base plate, a spherical bearing guide rail bracket, a spherical bearing guide rail, a test shaft bearing bracket, a load equalization system, a crank-rocker test system, a crank bearing bracket, a transmission system, a drive gear bearing bracket, an output gear bearing bracket, a motor bracket, a load equalization nut bracket, a load equalization double-headed screw bearing bracket, a worm gear bearing bracket, a load equalization gear bearing bracket, and an intermediate drive gear bearing bracket.

[0053] See Figure 3 , Figure 4 , Figure 5 The loading head 51 has a hole for mounting the loading shaft 57. A spring bracket for mounting the load-equalizing spring 52 is machined on the loading head 51. One end of the loading shaft 57 is installed in the hole on the loading head 51. The shaft end of the loading shaft 57 passes through the inner ring 54 of the spherical plain bearing. The inner ring 54 and the outer ring 53 of the spherical plain bearing are fitted together. The bottom of the outer ring 53 is fixedly connected to the dovetail pin 55 of the spherical plain bearing. The side of the outer ring 53 is fixedly connected to the loading weight 56 ​​of the spherical plain bearing. The hooks at both ends of the load-equalizing spring 52 are respectively hung on the spring brackets for mounting the load-equalizing spring 52 machined on the loading head 51, which are symmetrically arranged on the left and right sides. The loading shaft 57... The other end is installed in the corresponding mounting hole of the loading shaft and the load equalizing nut connecting block 58. The other pin hole on the loading shaft and the load equalizing nut connecting block 58 is aligned with the pin hole opened on the load equalizing nut 510 and connected by the load equalizing pin 59. The load equalizing nut 510 is machined with dovetail pins on the top and bottom. The load equalizing nut 510 and the load equalizing double-ended screw 515 form a screw-nut fit. The turbine 513 is installed in the middle section of the load equalizing double-ended screw 515 and connected by a key. The load equalizing double-ended screw bearings 514 are symmetrically installed on both sides of the middle section of the load equalizing double-ended screw 515. The worm 512 and the turbine 513 form a turbine-worm fit. The worm bearing 511 is installed on the optical shaft section of the worm 512.

[0054] See Figure 6 , Figure 7 , Figure 8 , Figure 9 , Figure 10The bottom of the sample box 61 has a mounting hole for a spherical bearing loading weight 56, which is installed in the mounting hole. A torque sensor connector 62 is installed on the side of the sample box 61. The top of the sample box 61 has a hole for installing a shim sample 65. Threads are machined into the hole for installing the shim sample 65. One end face of the shim sample 65 is fitted to the bottom end face of the hole for installing the shim sample 65 in the top of the sample box 61. The sample clamping nut 66 is screwed into the threaded hole for installing the shim sample 65 in the top of the sample box 61 until the bottom face is fitted and the other end face of the shim sample 65 is clamped, thus completing the installation of the shim sample 65. The annular end face of the annular test piece 64 is centered. The other end face of the gasket sample 65 forms an annular end face contact. An annular test piece 64 has an annular test piece groove 627 and an annular test piece mounting shaft 628. The annular test piece mounting shaft 628 is installed in the annular test piece mounting hole 629. An annular test piece locking pin 630 is machined on the annular test piece mounting hole 629. The annular test piece groove 627 on the annular test piece 64 engages with the annular test piece locking pin 630 on the annular test piece mounting hole 629. The inner ring of the crank bearing 67 is installed on the crank drive shaft 68. One end of the crank drive shaft 68 is installed in the crank hole 616. The crank screw 611 passes through the hole on the crank length adjusting slider 612. The crank length adjusting slider 612 is installed... The crank length adjusting slider 612 is installed in the crank length adjusting slider groove 615. A crank length adjusting slider plug 613 is installed at the bottom of the crank length adjusting slider 612. The crank length adjusting slider plug 613 passes through a corresponding hole in the middle section of the crank and is fixed by a crank length adjusting slider plug nut 614, thus restricting the sliding of the crank length adjusting slider 612. The crank screw 611 passes through a hole on the crank length adjusting slider 612 and then continues through a corresponding hole at one end of the connecting rod 610. A crank nut 69 is installed on the crank screw 611. A corresponding hole at the other end of the connecting rod 610 aligns with a corresponding hole at one end of the rocker arm. Rocker arm screws 618 pass through the aforementioned corresponding holes. A rocker arm nut 617 is installed on the rocker arm screw 618. A ratchet is machined on the rocker arm 619. A pawl slider groove 624 is formed, and a pawl slider 625 is installed within the pawl slider groove 624 to form a sliding connection pair. A pawl slider pin 620 is installed on the pawl slider 625. The pawl slider pin 620 passes through a corresponding hole machined on the rocker arm 619 and is fixed by a pawl slider pin nut 626. The pin hole on the pawl 622 is aligned with the corresponding hole on the pawl slider 625. The pawl pin 623 passes through the aforementioned holes in sequence, allowing the pawl 622 to rotate relative to the pawl slider 625. The pawl 622 and the ratchet wheel 621 form a ratchet pawl engagement. An external spline shaft section 631 is machined on the experimental shaft. A sliding spline limiting stop 641 is machined on the external spline shaft section 631. The sliding spline 632 engages with the external spline shaft section 631.The experimental shaft has a rocker arm and an idle shaft section 633 machined on it. An idle shaft hole section 636 is mounted on the rocker arm and experimental shaft idle shaft section 633. An idle shaft positioning step hole section 637 and an idle shaft positioning step shaft section 640 form a fit to restrict the axial freedom of the rocker arm. An inner spline hole section 635 of the rocker arm indirectly drives the experimental shaft through a fit with a sliding spline 632. A ratchet sliding shaft section 634 is machined on the experimental shaft, and a ratchet sliding key 63 is machined on the ratchet sliding shaft section 634. 9. A ratchet limiting stop 638 is machined on the ratchet sliding shaft section 634. The ratchet 621 is mounted on the ratchet sliding shaft section 634 and forms a fit with the ratchet sliding key 639 through a keyway machined on the ratchet 621. Both the sliding spline 632 and the ratchet 621 can slide on the experimental shaft, and both the sliding spline 632 and the ratchet 621 can drive the experimental shaft to rotate. The annular test specimen mounting hole 629 is fixedly connected to the experimental shaft to form a whole. The inner ring of the experimental shaft bearing 63 is mounted on the corresponding bearing mounting position on the experimental shaft.

[0055] See Figure 11 , Figure 12 , Figure 13The inner ring of the load output bearing 81 is mounted on the worm gear 512, and the outer ring of the load output bearing 81 is mounted on the load output bearing bracket 82. The load output gear 83 is mounted on the overhang of the worm gear 512, and the load output gear 83 and the load input gear 84 form a gear engagement. The load input gear 84 is mounted on the splined hole and smooth hole integrated shaft 819 to form a fixed connection. The splined hole and smooth hole integrated shaft 819 has a splined hole section and a smooth hole section machined in its inner cavity. The splined hole and smooth hole integrated shaft 819 is mounted on the inner ring of the load input bearing 85. The shift spline 8... One end of the shift spline 86 is installed inside the integrated shaft 819 with a spline hole and a smooth hole. The shift spline 86 can either rotate freely in the smooth hole section of the integrated shaft 819 or slide to rotate with the integrated shaft 819 in the spline hole section. The shift spline 86 passes through the spline hole 820 of the intermediate drive spur gear. The intermediate drive spur gear 89 has a spline hole 820 machined in the middle. The intermediate drive spur gear 89 and the output gear 818 form a gear engagement. The output gear 818 is mounted on the motor. The output shaft of motor 87 is connected to the output shaft via a key. The output shaft of motor 87 is mounted on the inner ring of output gear bearing 88. The other end of shift spline 86 is mounted inside spline-hole integrated shaft 819. The other end of shift spline 86 can either idle in the open section of spline-hole integrated shaft 819 or slide to drive spline-hole integrated shaft 819 to rotate together with the spline-hole integrated shaft 819. One end of spline-hole integrated shaft 819 is mounted on the inner ring of intermediate drive gear bearing 810. The other end is installed on the hole of the intermediate drive bevel gear 811. The intermediate drive bevel gear 811 and the drive bevel gear 812 form a bevel gear engagement at a 90° angle. The drive bevel gear 812 is installed on the drive shaft 817. The drive shaft 817 is installed on the inner ring of the drive gear bearing 816. The other end of the drive shaft 817 is installed on the drive spur gear 815. The drive spur gear 815 forms a gear engagement with the crank spur gear 814. The crank spur gear 814 is installed on the crank drive shaft 68. One end of the crank drive shaft 68 is installed on the inner ring of the crank bearing 813.

[0056] See Figure 1 A schematic diagram of the overall structure of the crank-rocker type end face friction and wear testing machine of the present invention, taken from the front isometric projection. Figure 2This invention provides a schematic diagram of the isometric structure of a crank-rocker type end-face friction and wear testing machine. A dovetail pin 55 of a spherical plain bearing is installed in a dovetail groove on a spherical plain bearing guide rail 3 to form a sliding connection pair. The spherical plain bearing guide rail 3 is mounted on a spherical plain bearing guide rail bracket 2, which is mounted on a base plate 1. The outer ring of the experimental shaft bearing 63 is mounted on an experimental shaft bearing bracket 4, which is mounted on the base plate 1. The outer ring of the crank bearing 67 is mounted on a crank bearing bracket 7, which is mounted on the base plate 1. The outer ring of the drive gear bearing 816 is mounted on a drive gear bearing bracket 9, which is mounted on the base plate 1. The outer ring of the output gear bearing 88 is mounted on an output gear bearing bracket 10, which is mounted on... On base plate 1, motor 87 is mounted on motor bracket 11, motor bracket 11 is mounted on base plate 1, load-equalizing nut 510 is mounted in the double dovetail groove on load-equalizing nut bracket 12, load-equalizing nut bracket 12 is mounted on base plate 1, the outer ring of load-equalizing double-ended screw bearing 514 is mounted on load-equalizing double-ended screw bearing bracket 13, load-equalizing double-ended screw bearing bracket 13 is mounted on base plate 1, the outer ring of worm bearing 511 is mounted on worm bearing bracket 14, worm bearing bracket 14 is mounted on base plate 1, the outer ring of loading input end bearing 85 is mounted on load-equalizing gear bearing bracket 15, load-equalizing gear bearing bracket 15 is mounted on base plate 1, the outer ring of intermediate drive gear bearing 810 is mounted on intermediate drive gear bearing bracket 16, intermediate drive gear bearing bracket 16 is mounted on base plate 1.

[0057] The specific steps of using the crank-rocker type end face friction and wear testing machine of the present invention are as follows:

[0058] First, install the crank-rocker experimental system 6. Place the shim sample 65 flat into the sample box 61. Then, use an Allen wrench to turn the sample clamping nut 66 until it is screwed into the sample box 61 and the shim sample 65 is clamped. At this point, the installation and tightening of the shim sample 65 in the sample box 61 is complete. Install the sliding spline 632 on the outer spline section 631 of the experimental shaft. Fix the sliding spline limiting stop 641 to one end of the outer spline section 631 of the experimental shaft, so that it, together with the outer end face of the rocker and experimental shaft idle positioning step section 640, limits the left and right sliding limit position of the sliding spline 632. Install the rocker and experimental shaft idle hole section 636 on the rocker and experimental shaft idle shaft section 633 until the rocker and experimental shaft idle positioning step section 637 and the rocker and experimental shaft are aligned. The rocker arm 619 is fixed on the experimental shaft until it engages with the experimental shaft's free-spinning positioning step section 640, near the sliding spline 632. Then, the other rocker arm is fixed to the experimental shaft's free-spinning positioning step section 640. At this point, the rocker arm 619 is installed on the experimental shaft, allowing it to rotate freely relative to the experimental shaft without axial movement. The ratchet 621 is then installed on the experimental shaft's ratchet sliding section 634, with the keyway on the ratchet 621 engaging with the ratchet slide key 639. The ratchet limiting stop 638 is then fixed to one end of the ratchet slide key 639. At this point, the ratchet limiting stop 638, along with the rocker arm near the ratchet sliding section 634 and the experimental shaft's free-spinning positioning step section 640, together limit the left and right sliding limits of the ratchet 621. The ratchet 621 can now drive the experimental shaft to rotate. Two identical annular test specimen mounting holes 629 shaft segments are fixed to both ends of the experimental shaft. The annular test specimen mounting shafts 628 of the two identical annular test specimens 64 are respectively installed into the annular test specimen mounting holes 629 at both ends of the experimental shaft, and the annular test specimen slots 627 on the annular test specimens 64 are aligned with the annular test specimen locking pins 630 to complete the installation and fastening of the annular test specimens 64. The pawl slider 625 is installed into the corresponding pawl slider groove 624 on the rocker arm 619, and the pawl slider pin 620 on the pawl slider 625 is inserted into the corresponding pin hole on the rocker arm 619. The pawl 622 is installed into the corresponding pin hole on the pawl slider 625 using the pawl pin 623, allowing the pawl 622 to move relative to the pawl slider 625. By rotating the ratchet slider 625 along the ratchet slider groove 624 to a suitable position, and simultaneously rotating the ratchet 622 until it engages with the ratchet wheel, the ratchet and pawl are engaged. Then, the two ratchet slider bolt nuts 626 are fixed to the ratchet slider bolts 620 to restrict the sliding of the ratchet slider 625. This completes the installation of the ratchet and pawl assembly. During the experiment, if intermittent circumferential end-face friction wear needs to be simulated, the ratchet 621 is slid close to the rocker arm near the ratchet sliding shaft section 634 and the experimental shaft's free-spinning positioning step shaft section 640 to engage the ratchet and pawl. Simultaneously, the sliding spline 632 needs to be slid close to one end of the sliding spline limiting plate 641. The intermittent motion angle of the intermittent circumferential rotation can be adjusted by changing the position of the ratchet slider 625.By reversing the pawl 622, the ratchet 621 can be controlled to drive the experimental shaft to rotate forward or backward. During the experiment, if it is necessary to simulate the friction and wear of the reciprocating oscillating end face, the ratchet 621 should be slid to one end close to the ratchet limit plate 638, disengaging the ratchet and pawl. Simultaneously, the sliding spline 632 needs to be slid to the rocker arm near the outer spline section 631 of the experimental shaft, and the experimental shaft should be positioned at the idle positioning step section 640, so that the outer spline of the sliding spline 632 and the inner spline hole section 635 of the rocker arm 619 are aligned. When the rocker arm 619 is engaged, it drives the sliding spline 632 to reciprocate, which in turn drives the experimental shaft to reciprocate, simulating the friction and wear of the reciprocating end face. The inner rings of the two experimental shaft bearings 63 are respectively installed onto the corresponding bearing mounting sections of the experimental shaft, and the outer rings of the two experimental shaft bearings 63 are respectively installed onto two identical experimental shaft bearing brackets 4. The experimental shaft bearing brackets 4 are fixed to the base plate 1. The other end of the rocker arm 619 is connected to the rocker arm nut 617 and the rocker arm screw 61. Connect one end of the connecting rod 610 to allow the rocker arm 619 to rotate freely relative to the connecting rod 610. Connect the other end of the connecting rod 610 to the crank length adjusting slider 612 via the crank nut 69 and the crank screw 611 to allow the connecting rod 610 to rotate freely relative to the crank length adjusting slider 612. Install the crank length adjusting slider 612 in the crank length adjusting slider groove 615 and insert the crank length adjusting slider pin 613 on the crank length adjusting slider 612 into the corresponding pin hole on the crank. Adjust the crank length adjusting slider 612 to the appropriate position according to the experimental requirements and then fix the crank length adjusting slider 612 with four crank length adjusting slider pin nuts. Fix the crank hole 616 to the crank drive shaft 68. Install the crank drive shaft 68 on the inner ring of the crank bearing 67. Install the outer ring of the crank bearing 67 on the crank bearing bracket 7 and fix it on the base plate 1. At this time, the installation of the crank rocker experimental system 6 is completed. ,

[0059] Then install the load equalization system 5, insert two identical spherical plain bearing dovetail pins 55 into the dovetail grooves on both sides of the spherical plain bearing guide rail 3 to form a sliding connection pair, fix the spherical plain bearing guide rail 3 to the spherical plain bearing guide rail bracket 2 and fix it to the base plate 1 through the spherical plain bearing guide rail bracket 2, align and install the spherical plain bearing loading weight 56 ​​into the mounting hole at the bottom of the pre-installed sample box 61 assembly, install two identical loading shafts 57 onto the inner ring 54 of the spherical plain bearing, insert one end of the loading shaft 57 into the corresponding mounting hole of the loading head 51, and attach the spring hooks on both sides of the load equalization spring 52 respectively. Hang the load on the corresponding position on the loading head 51, and push the two spherical bearings along the spherical bearing guide rail 3 to a suitable position so that the annular test piece 64 is in uniform contact with the end face of the gasket test piece 65 in the test piece box 61 assembly. Install the loading shaft and load equalization nut connecting block 58 on the other end of the loading shaft 57. Insert a load equalization nut 510 into the dovetail groove of the load equalization nut bracket 12 through its dovetail pin to form a sliding connection pair. Align the corresponding hole on the load equalization nut 510 with the corresponding hole on the loading shaft and load equalization nut connecting block 58, and then connect them with the load equalization pin. Screw one end of the load equalization double-ended screw 515 into the installed load equalization nut. After threading the nut 510 into the appropriate position, install the load-equalizing double-ended screw bearing 514, turbine 513, and load-equalizing double-ended screw bearing 514 onto the corresponding positions on the load-equalizing double-ended screw 515 in sequence. The outer rings of the load-equalizing double-ended screw bearings 514 on both sides are respectively installed onto two identical load-equalizing double-ended screw bearing brackets 13 and fixed to the base plate 1 by the load-equalizing double-ended screw bearing brackets 13. The turbine 513 is fixed to the middle of the load-equalizing double-ended screw 515 by a key connection. Insert another load-equalizing nut 510 into the dovetail groove of the load-equalizing nut bracket 12 through its dovetail pin to form a sliding connection pair and achieve load equalization. After aligning the corresponding hole on the nut 510 with the corresponding hole on the other loading shaft and the load-equalizing nut connecting block 58, connect them with another load-equalizing pin. Rotate the load-equalizing double-ended screw 515 so that its other end is screwed into the corresponding threaded hole of the other load-equalizing nut 510 until the relevant loading components on both sides are symmetrically arranged. Install the worm 512 to the corresponding position to form a worm-worm gear fit with the turbine 513. Install the smooth shaft sections at both ends of the worm 512 to the inner ring of the worm bearing 511. Install the outer ring of the worm bearing 511 to the worm bearing bracket 14 and fix it to the base plate 1 through the worm bearing bracket 14. At this time, the installation of the load-equalizing system is completed.

[0060] Next, install the transmission system 8. Pass the other end of the crank drive shaft 68 through the inner ring of the crank spur gear 814 and the crank bearing 813. The crank spur gear 814 is connected to the crank drive shaft 68 via a key. The outer ring of the crank bearing 813 is mounted on the crank bearing bracket 7 and fixed to the base plate 1 via the crank bearing bracket 7. The drive spur gear 815 forms a gear engagement with the crank spur gear 814. The drive spur gear 815 is mounted on one end of the drive shaft 817 via a key, and the other end passes sequentially through the inner ring of the drive gear bearing 816 and the drive bevel gear 812. The drive bevel gear 812 is connected to the drive shaft 817 via a key. The outer ring of the drive gear bearing 816 is mounted on the drive gear bearing bracket 9 and fixed to the base plate 1 via the drive gear bearing bracket 9. The drive bevel gear 812 and the intermediate drive bevel gear 811 form a bevel gear engagement at a 90° angle. The closed end of the splined hole integrated shaft 819 is fixedly installed on the intermediate drive bevel gear 811, and the other end passes through the inner ring of the intermediate drive gear bearing 810. The outer ring of the intermediate drive gear bearing 810 is installed on the intermediate drive gear bearing bracket 16 and fixed to the base plate 1 through the intermediate drive gear bearing bracket 16. One end of the shift spline 86 passes sequentially through the intermediate drive spur gear spline hole 820 machined at the center of the intermediate drive spur gear 89 and the splined hole integrated shaft 819. The other end of the shift spline 86 passes through another splined hole integrated shaft 819. The sealed end of the other splined hole integrated shaft 819 passes through the loading input bearing 8. 5. The inner ring of the loading input end gear 84 and the outer ring of the loading input end bearing 85 are mounted on the load-equalizing gear bearing bracket 15 and fixed to the base plate 1 through the load-equalizing gear bearing bracket 15. The intermediate drive spur gear 89 and the output gear 818 form a gear engagement. The output gear 818 is mounted on one end of the output shaft of the motor 87 and connected by a key. The middle section of the output shaft of the motor 87 passes through the inner ring of the output gear bearing 88. The outer ring of the output gear bearing 88 is mounted on the output gear bearing bracket 10 and fixed to the base plate 1 through the output gear bearing bracket 10. The motor 87 is mounted on the motor bracket 11 and fixed to the base plate 1 through the motor bracket 11. The loading input end gear 84 and the loading output end gear 83 form a gear engagement. The loading output end gear 83 is connected to the base plate 1 through the load-equalizing gear bracket 15. A key is connected to the optical shaft portion at the other end of the worm gear 512. The middle section of the optical shaft portion at the other end of the worm gear 512 is mounted on the inner ring of the load output bearing 81. The outer ring of the load output bearing 81 is mounted on the load output bearing bracket 82 and fixed to the base plate 1 by the load output bearing bracket 82. The length of the shift spline 86 is specific. When loading is required, the shift spline 86 is slid to the end of the integrated spline hole shaft 819 near the load input gear 84 so that the shift spline 86 engages with the inner spline hole section of the integrated spline hole shaft 819. At this time, the length of the shift spline 86 is just enough to place the other end of the spline within the optical hole section of the integrated spline hole shaft 819 near the middle drive bevel gear 811 and can rotate freely relative to the optical hole section.At this point, the intermediate drive spur gear 89 transmits power to the worm gear loading section via the shift spline 86. Conversely, when an experiment is required, the shift spline 86 is slid to the other end, at which point the intermediate drive spur gear 89 transmits power to the crank rocker experimental section via the shift spline 86. This completes the installation of the entire machine.

[0061] During the formal experiment, after the sample is installed according to the experimental requirements, the length of the crank and the position of the pawl are adjusted. The experimental type is selected as reciprocating oscillating end face friction wear or intermittent circumferential end face friction wear. Then, the shift spline is slid to the loading end to uniformly load the loading system, ensuring the symmetry and uniformity of the contact load on the end faces of the test specimens at both ends of the experimental shaft. After loading is completed, the shift spline is slid to the crank rocker experimental system end to conduct the experiment, simulating reciprocating oscillation or intermittent circumferential end face friction wear conditions.

[0062] The present invention provides a crank-rocker type end face friction and wear testing machine, which has the advantages of large load adjustment range, large torque transmission, stable and symmetrical load application, high control precision, adjustable reciprocating swing angle, adjustable intermittent rotation angle, and the ability of the testing device to simulate the end face friction and wear of two samples in a single test, and greatly shortens the test time.

[0063] The above is an exemplary description of the invention. Obviously, the specific implementation of the invention is not limited to the above-described manner. Any non-substantial improvement made using the inventive concept and technical solution of the invention, or the direct application of the inventive concept and technical solution to other situations without modification, is within the protection scope of the invention.

Claims

1. A crank-rocker type end-face friction and wear testing machine, characterized in that, It includes a frame, a load sharing system (5), a crank-rocker experimental system (6) and a transmission system (8), each system being mounted on the frame, which provides mounting support for each system; The load equalization system (5) is used to adjust the contact pressure of the end face friction wear specimen and to ensure the uniformity of the load applied at both ends. The crank-rocker experimental system (6) is used to switch between simulating reciprocating oscillating end face friction and wear or intermittent end face circumferential friction and wear, and can simultaneously simulate end face friction and wear of two samples in a single experiment. The transmission system (8) is used to selectively provide power for the load application of the load-sharing system (5) or the motion drive of the crank-rocker experimental system (6) by shifting gears; The load equalization system (5) includes a loading head (51), a load equalization hanging spring (52), a joint bearing assembly, a loading shaft (57), a load equalization adjustment assembly, and a joint bearing loading weight (56). The loading head (51) is provided with a hanging spring frame, and the two ends of the load-equalizing hanging spring (52) are respectively hung on the hanging spring frames of two symmetrically arranged loading heads (51); One end of the loading shaft (57) is connected to the loading head (51), and the other end is connected to the load equalization adjustment assembly through the load equalization nut connecting block (58) and the load equalization pin (59). The load equalization adjustment assembly includes a load equalization nut (510), a load equalization double-ended screw (515), a turbine (513), and a worm gear (512). The load-equalizing double-ended screw (515) has load-equalizing double-ended screw bearings (514) symmetrically installed on both sides of the middle section, and the worm (512) has a worm bearing (511) installed on the optical axis section. The dovetail pin (55) of the spherical bearing and the spherical bearing guide rail (3) on the frame form a sliding connection pair. The crank-rocker experimental system (6) includes an experimental shaft, a sample clamping assembly, a crank assembly, a connecting rod (610), a rocker (619), and a working condition switching assembly; The sample clamping assembly includes annular test pieces (64) symmetrically installed at both ends of the experimental shaft and a sample box (61) for fixing the shim sample (65). The crank assembly includes a crank drive shaft (68), a crank length adjustment slider (612), a crank length adjustment slider plug (613), and a crank length adjustment slider plug nut (614). One end of the connecting rod (610) is hinged to the crank length adjusting slider (612) via the crank screw (611) and crank nut (69), and the other end is hinged to one end of the rocker (619) via the rocker screw (618) and rocker nut (617); The working condition switching component includes a sliding spline (632), a ratchet (621), a pawl (622), and a pawl slider (625). The experimental shaft is provided with a rocker arm and an experimental shaft idle shaft section (633). The rocker arm (619) is provided with a rocker arm and experimental shaft idle hole section (636) that cooperates with the idle shaft section and a rocker arm and experimental shaft idle positioning step hole section (637). The rocker arm and experimental shaft idle positioning step hole section (637) cooperates with the rocker arm and experimental shaft idle positioning step shaft section (640) on the experimental shaft to restrict the axial degree of freedom of the rocker arm (619). The annular test specimen (64) is provided with an annular test specimen slot (627) and an annular test specimen mounting shaft (628). The test shaft is provided with an annular test specimen mounting hole (629) and an annular test specimen locking pin (630). The annular test specimen mounting shaft (628) is inserted into the annular test specimen mounting hole (629). The annular test specimen slot (627) and the annular test specimen locking pin (630) are engaged and fixed. The top of the sample box (61) is provided with a mounting hole with internal threads. The gasket sample (65) is pressed and fixed in the mounting hole by the sample clamping nut (66). The side of the sample box (61) is provided with a torque sensor connector (62). The pawl slider (625) is slidably engaged with the rocker arm (619) through the pawl slider groove (624). The pawl (622) is hinged to the pawl slider (625) through the pawl pin (623). The pawl slider (625) is provided with a pawl slider plug (620) and a pawl slider plug nut (626) for locking the position of the pawl slider (625).

2. The crank-rocker type end-face friction and wear testing machine according to claim 1, characterized in that, The transmission system (8) includes a motor (87), a shift spline (86), a spline hole and smooth hole integrated shaft (819), and a gear transmission assembly; The output shaft of the motor (87) is equipped with an output gear (818), and the gear transmission assembly includes an intermediate drive spur gear (89), an intermediate drive bevel gear (811), a drive bevel gear (812), a drive spur gear (815), and a crank spur gear (814).

3. The crank-rocker type end-face friction and wear testing machine according to claim 2, characterized in that, The output shaft of the motor (87) is equipped with an output gear bearing (88), the drive shaft (817) is equipped with a drive gear bearing (816), the loading input end gear (84) is equipped with a loading input end bearing (85), the intermediate drive spur gear (89) is equipped with an intermediate drive gear bearing (810), the worm (512) is equipped with a loading output end bearing (81), and the crank drive shaft (68) is equipped with a crank bearing (813). The outer ring of each bearing is mounted on the frame through a corresponding bearing bracket.

4. The crank-rocker type end-face friction and wear testing machine according to claim 1, characterized in that, The frame includes a base plate (1) and a spherical bearing guide rail bracket (2), an experimental shaft bearing bracket (4), a crank bearing bracket (7), a motor bracket (11), a load-equalizing nut bracket (12), a load-equalizing double-headed screw bearing bracket (13), a worm bearing bracket (14), a load-equalizing gear bearing bracket (15), and an intermediate drive gear bearing bracket (16) mounted on the base plate (1). Each bracket provides installation support for the corresponding component.

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