Lubrication performance observation test device and method for intermediate bearing lubrication structure under inner and outer ring rotation

Abstract

The present invention belongs to the technical field of bearing testing, and proposes a device and method for observing the lubrication performance of an intermediate bearing lubrication structure under rotating inner and outer rings. A motor is used to rotate the inner ring of the intermediate bearing, and another motor is used to rotate the bevel gear, thereby driving the outer ring of the bearing under test to rotate, achieving synchronous rotation of the inner and outer rings of the intermediate bearing. A distributed oil return structure is used on the left and right sides of the intermediate bearing, and is combined with a flow sensor and an oil chip sensor to measure the return oil flow and wear characteristics of the left and right sides of the intermediate bearing. By monitoring the return oil flow on both sides of the intermediate bearing and combining it with temperature measurements on both sides of the intermediate bearing, a relationship between the flow field characteristics and temperature characteristics of the intermediate bearing is established. A lubrication oil return structure under the intermediate bearing is used, and a high-speed camera is used to collect image information, so that the under-ring lubrication flow characteristics and the flow distribution characteristics on the left and right sides of the intermediate bearing caused by the under-ring lubrication can be observed, thereby providing support for the guide design of the bearing lubrication structure.

Description

Technical Field

[0001] The present invention relates to the technical field of bearing testing, and in particular to a device and method for observing the lubrication performance of an intermediate bearing lubrication structure under rotation of inner and outer rings. Background Art

[0002] The intermediate bearing is one of the key components that affects the rotational performance of machinery. Most of the dual-rotor engines currently in service at home and abroad use cylindrical roller bearings with synchronously rotating inner and outer rings. The lubricity of the intermediate bearing is crucial to the flow characteristics inside the bearing, which directly affects the friction characteristics and heat dissipation characteristics of the interface where the lubricating oil reaches. The friction characteristics in turn affect the degree of wear between bearing parts, and the heat dissipation characteristics are directly related to the temperature characteristics of the bearing. It is of great significance to carry out experimental research on the lubrication performance of the intermediate bearing lubrication structure.

[0003] Although there are some bearing testers for bearing lubricants, most of them are not convenient for observing the lubrication performance of the lubricating structure. For example, the patent: Rolling bearing lubrication working condition experimental simulation device and measurement method (CN102353334A) mainly measures and analyzes the bearing motion state, but does not focus on the flow characteristics and temperature characteristics of the lubricant; the patent: Rolling bearing lubrication simulation experimental device (CN202189050U) can simulate the on-site working conditions of heavy-load rolling bearings and place multiple sets of experimental bearings at the same time, but its monitoring system cannot well observe the various characteristics of the lubricant, but only monitors the effects of various lubricants and greases on bearing performance; the patent: Rolling bearing lubrication simulation experimental device (CN202189050U) can simulate the on-site working conditions of heavy-load rolling bearings and place multiple sets of experimental bearings at the same time, but its monitoring system cannot well observe the various characteristics of the lubricant, and only monitors the effects of various lubricants and greases on bearing performance; An oil film thickness test device and test method (CN103615994A) employs ultrasonic film thickness measurement technology to obtain real-time film thickness values at the contact points of rolling bearings under the influence of slip. This method measures the oil film formed by the lubricating oil and does not emphasize the flow characteristics of the lubricating oil itself. A patented device and method for visualizing bearings (CN110307979A) utilizes fully transparent outer end covers and inner oil seals to enable full visualization and real-time monitoring of bearing operation and lubrication conditions under different operating conditions. However, this test device does not simulate the synchronous rotation of the inner and outer rings of aviation intermediate bearings and cannot capture the lubrication flow characteristics of cylindrical roller bearings under eccentric loads.

[0004] In summary, there is currently no test device to study the rebound of lubricating oil, heat dissipation and flow conditions on both sides of the intermediate bearing when the inner and outer rings are selected. Therefore, it is necessary to study a test device and method for observing the lubrication performance of the intermediate bearing lubrication structure under the rotation of the inner and outer rings to provide support for the optimal design of the lubricating oil and bearing structure. Summary of the Invention

[0005] The present invention aims to address the deficiencies in the prior art and proposes a lubrication performance observation test device and method for an intermediate bearing lubrication structure under rotation of inner and outer rings based on machine vision. In addition, the lubrication performance observation test device for a cylindrical roller bearing lubrication structure has synchronous rotation of inner and outer rings, an oil supply system, an oil return monitoring system, and a temperature measurement system. At the same time, the flow characteristics of the lubricating oil inside the tested bearing can be effectively observed by using a tracer factor.

[0006] The technical solution of the present invention: A lubrication performance observation test device for the intermediate bearing lubrication structure under the rotation of inner and outer rings includes an inner ring drive system 1, an outer ring drive system 2, an intermediate bearing system 3, an oil injection system 4, an oil return system 5, a temperature measurement system 6, an intermediate bearing sleeve support system 7, an observation system 8, a box 9 and a test bench base 10; the inner ring drive system 1, the box 9 and the observation system 8 are installed on the test bench base 10 in sequence.

[0007] The box body 9 includes a left end cover 91, a shell body 92 and a right glass end cover 93 of the box body; the shell body 92 is a split structure, installed on the test bench base 10, and its two ends are respectively connected to the left end cover 91 and the right glass end cover 93 of the box body; the intermediate bearing system 3, the oil return system 5, the temperature measurement system 6, and the intermediate bearing sleeve support system 7 are all installed inside the box body 9; a notch is provided at the top of the shell body 92 for fixing the outer ring drive system 2; a through hole is drilled on the upper part of the left end cover 9 of the box body for connecting the oil injection system 4 to transport lubricating oil; the right glass end cover 93 of the box body is used to observe the movement state between the contact surfaces of the tested bearings of the shell body 92.

[0008] The inner ring drive system 1 is mainly composed of a motor base 11, a servo motor a12, a coupling a13, a support bearing seat system 14 and a stepped main shaft 15; one end of the stepped main shaft 15 is connected to the servo motor a12 through the coupling a13, and the other end is connected to the inner ring of the intermediate bearing 32; the servo motor a12 transmits torque to the stepped main shaft 15 through the coupling a13, thereby driving the inner ring of the intermediate bearing 32 to rotate. The support bearing seat system 14 is installed on the stepped main shaft 15, and the support bearing seat system 14 is fixed to the test bench base 10 through a T-shaped workbench; the servo motor a12 is fixed to the test bench base 10 through the motor base 11; the servo motor a12 transmits torque to the stepped main shaft 15 through the coupling a13, thereby driving the inner ring of the intermediate bearing 32 to rotate; the support bearing seat system 14 includes a deep groove ball bearing a141, a bearing seat a142, a pressure cover a143 and a sleeve 144; the bearing seat a1 Bearing seat a142 is mounted on the stepped spindle 15, with a gap between them. Gland a143 is fixed at both ends of the bearing seat a142. Two deep groove ball bearings a141 are installed in the gap between the bearing seat a142 and the stepped spindle 15. They position and support the stepped spindle 15, limiting axial movement and bearing the primary load of the stepped spindle 15, preventing significant deflection. A sleeve 144 is installed between the two deep groove ball bearings a141 on the stepped spindle 15 to axially secure them. Bearing seat a142 is bolted to the test bench base 10, providing support for the two deep groove ball bearings a141 on the spindle.

[0009] The outer ring drive system 2 mainly consists of a servo motor b21, a coupling b22, a motor bracket 23, a flange 24, a gear shaft 25, a driving bevel gear 26, a deep groove ball bearing b27, a bearing sleeve 28, a bearing seat b29 and a pressure cover b30. The output shaft of the servo motor b21 is connected to the coupling b22, the gear shaft 25 and a pair of driving bevel gears 26 in sequence. The driving bevel gear 26 meshes with the driven bevel gear 523 welded to the intermediate bearing sleeve 524. The intermediate bearing sleeve 524 is located outside the outer ring of the intermediate bearing 32 and is in transitional fit with it. The gear shaft 25 is sleeved with a bearing seat b27. 29, there is a gap between the two; the bearing seat b29 and the pressure cover b30 form a closed space; the bearing sleeve 28 and two deep groove ball bearings b27 are sequentially installed in the closed space from the outside to the inside; the end of the bearing seat b29 passes through the notch of the housing 92, and its side is fixed to the housing 92 through the flange 24; the servo motor b21 is fixed to the housing 92 through the motor bracket 23; the servo motor b21 transmits the torque to the gear shaft 25 through the coupling b22, and the gear shaft 25 drives the active bevel gear 26 to rotate, thereby rotating the intermediate bearing sleeve 524, and finally driving the outer ring of the intermediate bearing 32 to rotate.

[0010] The intermediate bearing system 3 primarily consists of an eccentric disc 31, an intermediate bearing 32, and a hydraulic cover 33. The inner side of the intermediate bearing 32 is fixedly connected to the hydraulic cover 33, which compresses the inner ring of the intermediate bearing 32 to prevent it from falling off or moving. The eccentric disc 31 is mounted on the outer side of the intermediate bearing 32 and engages in a groove provided in the intermediate bearing sleeve 524. As the intermediate bearing sleeve 524 rotates, it transmits centrifugal load to the intermediate bearing 32, thereby simulating the working environment of the intermediate bearing 32. The left side of the inner ring of the intermediate bearing 32 is positioned by the shoulder of the stepped main shaft 15, and adopts a basic hole system to achieve an interference fit with it. The high preload stiffness prevents excessive stress and deformation between the main shaft and the inner ring caused by transient overload during the intermediate bearing 32 testing.

[0011] The oil injection system 4 primarily consists of an under-ring side spray pipe 41, a pipe cover 42, an under-ring oil collecting ring 43, and a locking nut 44. The under-ring side spray pipe 41 is welded to the left end cap 91 of the housing and communicates with a through-hole in the left end cap 91. The under-ring side spray pipe 41 includes an under-ring pipe and a side spray pipe, each of which has a lubrication nozzle with a pipe cover 42 at one end. The under-ring oil collecting ring 43 is secured to the outside of the stepped main shaft 15 via a locking nut 44. The lubrication nozzle of the under-ring pipe is located above the under-ring oil collecting ring 43. The oil groove of the under-ring oil collecting ring 43 connects to the oil inlet at the bottom of the intermediate bearing 32 through the stepped main shaft 15. The lubrication nozzle of the side spray pipe is located on the side of the rotating element of the intermediate bearing 32. The lubrication nozzle of the side spray pipe sprays oil toward the rotating element of the intermediate bearing 15. The lubrication nozzle of the under-ring pipe delivers lubricating oil through the oil groove at the bottom of the under-ring oil collecting ring 43 into the oil inlet at the bottom of the intermediate bearing 32, where it is then transported into the bearing under test.

[0012] The oil return system 5 is mainly composed of a left oil return system 51, a right oil return system 52, an oil chip sensor 53 and a flow sensor 54; the left oil return system 51 is located on one side of the intermediate bearing 32, and its left oil leakage pipe is embedded in the bottom of the box body 9 and extends out from the left end cover 91 of the box body, which is used to collect the lubricating oil rebounded from one side of the intermediate bearing 32; the right oil return system 52 is located on the other side of the intermediate bearing 32, and is used to collect the lubricating oil sprayed from the other side of the intermediate bearing 32; the right oil return system 52 includes a temperature sensor pipe 521, an oil retaining ring 522, a driven bevel gear 523, an intermediate bearing sleeve 524, a through-hole gas-electric slip ring 525, an oil return pipe 526 and a spiral U-groove 527; the spiral U-groove 527 is embedded in the intermediate bearing sleeve 524, one end of which receives the lubricating oil sprayed from the other side of the intermediate bearing 32, and the other end is connected to the oil return pipe 52 in sequence 6 and the rotating end of the through-hole gas-electric slip ring 525, the through-hole gas-electric slip ring 525 is fixed on the outside of the intermediate bearing sleeve 524, and there is a gap between it and the driven bevel gear 523 to ensure the normal operation of the driven bevel gear 523; the stationary end of the through-hole gas-electric slip ring 525 is connected to the right oil leakage pipe; the right oil leakage pipe is embedded in the bottom of the box body 9 and then extends out from the right glass end cover 93 of the box body; the oil retaining ring 522 is fixed on the inside of the intermediate bearing sleeve 524, which is located on one side of the return oil pipe 526 to block the lubricating oil sprayed from the other side of the intermediate bearing 32 and concentrate the lubricating oil into the return oil pipe 526 below; the flow sensor 54 and the oil debris sensor 53 are arranged in sequence on the oil leakage pipe to measure the lubricating oil flow and wear on both sides of the intermediate bearing 32; the temperature sensor pipe 521 is arranged in the wall of the intermediate bearing sleeve 524, which includes a vertical through hole and a horizontal hole.

[0013] The temperature measurement system 6 includes a left temperature sensor 61 and a right temperature sensor 62; one end of the left temperature sensor 61 is connected to one side of the outer ring of the intermediate bearing 32, and the other end is connected to the rotating end of the through-hole gas-electric slip ring 525 through the horizontal hole of the temperature sensor pipe 521; one end of the right temperature sensor 62 is connected to the other side of the outer ring of the intermediate bearing 32, and the other end is connected to the rotating end of the through-hole gas-electric slip ring 525 through the vertical through-hole of the temperature sensor pipe 521; the left temperature sensor 61 and the right temperature sensor 62 respectively collect temperature comparison data on both sides of the outer ring of the intermediate bearing 32; the rotating end of the through-hole gas-electric slip ring 51 is connected to the internal data lines of the left and right temperature sensors, and the stationary end of the through-hole gas-electric slip ring 525 is connected to the external data line to output the temperature.

[0014] The tested bearing sleeve support system 7 includes a deep groove ball support bearing 71, a support bearing seat 72 and a hydraulic cover b73; the deep groove ball support bearing 71 and the intermediate bearing sleeve 524 are interference fit using a basic hole system; the support bearing seat 72 is sleeved on the outside of the deep groove ball support bearing 71 and fixedly connected to the box body 9; the hydraulic cover b73 is fixed between the support bearing seat 72 and the deep groove ball support bearing 71, and the intermediate bearing sleeve 524 is pressed against the inside of the hydraulic cover b73, thereby preventing the outer ring of the intermediate bearing 32 from falling off and moving.

[0015] The observation system 8 includes a coaxial light source 81, a CCD high-speed camera 82 and an observation base 83; the observation base 83 is connected to the test bench base 10 through a "J"-shaped workbench; the coaxial light source 81 and the CCD high-speed camera 82 are fixed on the observation base 83 in sequence; the coaxial light source 81 gathers the divergent light, and the CCD high-speed camera 82 realizes image acquisition of the lubrication condition of the measured bearing during operation.

[0016] The oil retaining ring 522 is located adjacent to the oil return pipe 526, concentrating the lubricating oil ejected from the right side to the oil return pipe below. Only the front sensing portion of the flow sensor 54 is located in the oil leakage pipe, while all the lubricating oil in the oil leakage pipe flows out through the oil debris sensor 53.

[0017] The test bench base 10 is provided with multiple tracks, and the inner ring driving system 1, the box 9 and the observation system 8 are moved on the tracks and then fixed.

[0018] One side of the inner ring of the intermediate bearing 32 is positioned by the shoulder of the stepped main shaft 15. The shoulder and the inner ring of the intermediate bearing 32 are interference fit in a basic hole system. The preload stiffness is set to avoid large stress deformation of the main shaft-inner ring due to instantaneous overload during the bearing test.

[0019] Only the front sensing portion of the flow sensor 54 is located in the oil leakage pipeline; all the lubricating oil in the oil leakage pipeline flows out of the oil leakage pipeline through the oil debris sensor 53.

[0020] A method for testing the lubrication performance of an intermediate bearing lubrication structure with inner and outer rings rotating comprises the following steps:

[0021] Step 1: Start servo motor a12 and servo motor b21 to rotate the stepped main shaft 15 and gear shaft 25, respectively, so that the inner and outer rings of the intermediate bearing 32 rotate synchronously. Apply an eccentric load to the intermediate bearing 32 via the eccentric disk 31 on the bearing sleeve 524 to simulate a working environment.

[0022] Step 2: By controlling the opening and closing of the pipe covers 42 at the under-ring pipe and the side-spray pipe, and cooperating with the left and right oil return systems 51 and 52, as well as the flow sensor 54 and the oil chip sensor 53 on both sides of the intermediate bearing 32, the return oil flow and wear characteristics on the left and right sides of the intermediate bearing 32 are monitored, thereby performing a comparative analysis of the flow supply conditions on both sides of the intermediate bearing 32 under three conditions: under-ring lubrication only, side-spray lubrication only, and simultaneous under-ring and side-spray lubrication.

[0023] Step 3: The through-hole gas-electric slip ring 525 is connected to the left temperature sensor 61 and the right temperature sensor 62 for monitoring the left and right temperatures of the outer ring of the intermediate bearing 32. The rotating end of the through-hole gas-electric slip ring 525 rotates with the intermediate bearing 32, and the stationary end outputs temperature data to collect the left and right temperatures of the outer ring of the intermediate bearing 32 during the lubrication process.

[0024] Step 4: Change lubrication parameters, monitor the oil return flow and wear on the left and right sides of the intermediate bearing 32 and the temperature on the left and right sides of the outer ring under different lubrication conditions; establish the relationship between the flow field characteristics, temperature characteristics, and wear characteristics of the intermediate bearing 32.

[0025] The lubrication parameters include the flow rate of the lubrication nozzle and the angle of the lubrication nozzle.

[0026] Beneficial effects of the present invention:

[0027] (1) The present invention proposes a test device for observing the lubrication performance of an intermediate bearing lubrication structure under rotation of the inner and outer rings. The device adopts an intermediate bearing under-ring lubrication oil collection structure and cooperates with a high-speed camera to collect image information. The device can observe the under-ring lubrication flow characteristics and the flow distribution characteristics on the left and right sides of the intermediate bearing caused by the under-ring lubrication, thereby providing support for the guide design of the bearing lubrication structure.

[0028] (2) The present invention uses a motor arrangement at one end to drive the inner ring of the intermediate bearing to rotate, and the universal gear shaft of the motor at the other end drives a pair of bevel gears to rotate, thereby driving the outer ring of the measured bearing to rotate, achieving synchronous rotation of the inner and outer rings of the intermediate bearing, while leaving observation space for the observation of the high-speed camera on the right;

[0029] (3) The present invention adopts a distributed oil return structure on the left and right sides of the intermediate bearing and cooperates with a flow sensor and an oil chip sensor to measure the return oil flow and wear characteristics on the left and right sides of the intermediate bearing, and compares and analyzes the flow supply conditions on both sides under the intermediate bearing ring and side spray lubrication conditions;

[0030] (4) The present invention can analyze the temperature change caused by the flow of the intermediate bearing and establish the relationship between the flow field characteristics and temperature characteristics of the intermediate bearing by monitoring the return oil flow on the left and right sides of the intermediate bearing and combining it with the temperature measurement on the left and right sides of the intermediate bearing;

[0031] (5) The present invention installs a through-hole gas-electric slip ring on the intermediate bearing sleeve, the upper end of which is connected to a temperature sensor, and the lower end is connected to an oil return pipe in conjunction with an oil retaining structure, thereby realizing the measurement of the temperature on the left and right sides of the outer ring of the intermediate bearing and the collection of the return oil flow on the right side. BRIEF DESCRIPTION OF THE DRAWINGS

[0032] Figure 1 This is a working principle diagram of the lubrication performance observation test device of the intermediate bearing lubrication structure under the rotation of the inner and outer rings of the present invention;

[0033] Figure 2 An overall cross-sectional view of a test device for observing the lubrication performance of an intermediate bearing lubrication structure with inner and outer rings rotating according to the present invention;

[0034] Figure 3 (a) is an axonometric view of the inner ring drive system;

[0035] Figure 3 (b) is a cross-sectional view of the inner ring drive system structure;

[0036] Figure 4 This is the structural diagram of the outer ring drive system;

[0037] Figure 5 This is the structural diagram of the intermediate bearing system;

[0038] Figure 6 (a) is a structural diagram of the fuel injection system;

[0039] Figure 6 (b) is a partial enlarged view of the fuel injection system;

[0040] Figure 7 (a) is a structural diagram of the oil return system;

[0041] Figure 7 (b) is a structural diagram of the intermediate bearing sleeve;

[0042] Figure 7 (c) is a partial enlarged view of the right oil return system;

[0043] Figure 7 (d) is a partial enlarged view of the left oil return system;

[0044] Figure 8 This is the structural diagram of the temperature measurement system;

[0045] Figure 9 This is an axonometric drawing of the intermediate bearing sleeve support system;

[0046] Figure 10 It is an axonometric diagram of the observation system;

[0047] Figure 11 This is the axonometric drawing of the box;

[0048] Figure 12 This is a schematic diagram of the test bench base;

[0049] Figure 13 This is the overall structure diagram of the test device for observing the lubrication performance of the intermediate bearing lubrication structure under the rotation of the inner and outer rings.

[0050] In the figure: 1-inner ring drive system; 2-outer ring drive system; 3-intermediate bearing system; 4-oil injection system; 5-oil return system; 6-temperature measurement system; 7-intermediate bearing sleeve support system; 8-observation system; 9-housing; 10-test bench base; 11-motor base; 12-servo motor a; 13-coupling a; 14-support bearing seat system; 15-stepped spindle; 141-deep groove ball bearing a; 142-bearing seat a; 143-pressure cover a; 144-sleeve; 21-servo motor b; 22-coupling b; 23-motor bracket; 24-flange; 25-gear shaft; 26-driving bevel gear; 27-deep groove ball bearing b; 28-bearing sleeve; 29-bearing seat b; 30-pressure cover b; 31-eccentric disk; 32-intermediate Intermediate bearing; 33-hydraulic cover; 41-lower side spray pipe of the ring; 42-pipe cover; 43-lower oil collecting ring of the ring; 44-locking nut; 51-left oil return system; 52-right oil return system; 53-oil chip sensor; 54-flow sensor; 521-temperature sensor pipe; 522-oil retaining ring; 523-driven bevel gear; 524-intermediate bearing sleeve; 525-through-hole gas-electric slip ring; 52-6 oil return pipe; 527-spiral U-groove; 61-left temperature sensor; 62-right temperature sensor; 71-deep groove ball support bearing; 7-2 support bearing seat; 73-hydraulic cover b; 81-coaxial light source; 82-CCD high-speed camera; 83-observation base; 91-left end cover of the box; 92-shell; 93-right glass end cover of the box. DETAILED DESCRIPTION

[0051] The specific implementation of the present invention is further described below in conjunction with the accompanying drawings and technical solutions.

[0052] It should be understood that the accompanying drawings are not drawn to scale but are merely simplified representations for the purpose of illustrating various features of the basic principles of the present invention. The specific design features of the present invention, including, for example, specific dimensions, orientations, positions, and configurations, will be determined in part by the specific intended application and use environment. In the multiple accompanying drawings, identical or equivalent components (elements) are referenced with the same reference numerals. In the description of the present invention, it should be noted that terms such as "center," "longitudinal," "lateral," "upper," "lower," "front," "back," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer" indicate positions or positional relationships based on those shown in the accompanying drawings. These terms are intended solely to facilitate description and simplify the present invention and are not intended to indicate or imply that the device or element referred to must have, be constructed, or operate in a specific orientation. Therefore, they should not be construed as limitations on the present invention.

[0053] Combine Figure 1The working principle is as follows: when the inner and outer rings of the intermediate bearing rotate synchronously, the speed of the inner ring is W1 and the speed of the outer ring is W2; the lubricating oil enters the interior of the intermediate bearing 32 through two lubrication methods: side spray and under-ring lubrication, and the flow rates are L 侧 and L 环 ; Part of the oil flows out from the right side through the intermediate bearing, and part is rebounded and flows out from the left side. In order to compare the return oil flow L on both sides 左 and L 侧 As well as the wear conditions C1 and C2 on both sides, the oil return systems on both sides are installed with flow sensors 54 and oil debris sensors 53; the through-hole gas-electric slip ring fixed on the intermediate bearing sleeve 524 is installed with temperature sensors to measure the inner ring temperature T1 and the outer ring temperature T2 of the intermediate bearing; by collecting and analyzing the experimental data of these three lubrication properties, the coupling relationship between them is obtained.

[0054] Combine Figure 2 The lubrication performance observation test device of the intermediate bearing lubrication structure under the rotation of the inner and outer rings is used. The servo motor a12 and the servo motor b21 are bidirectionally loaded and connected to the box body 9 through the coupling a13 and the coupling b22. The stepped main shaft 15 is installed with the intermediate bearing 32 to be tested. The box body 9 is installed with the oil injection system 4. The oil return system 5 is designed on the left and right sides of the intermediate bearing 32 and sensors are installed to monitor the temperature, flow and wear characteristics. The observation system 8 is installed on the test bench base 10 by bolts.

[0055] Referring to Figure 3 , the inner ring drive system 1 consists of a motor base 11, a servo motor a12, a coupling b13, a support bearing system 14, and a stepped spindle 15. The support bearing system 14 consists of a deep groove ball bearing a141, a bearing seat a142, a gland a143, and a sleeve 144. One end of the stepped spindle 15 is connected to the servo motor a12 via the coupling a13, and the other end is mounted with an intermediate bearing 32. Two deep groove ball support bearings a141 are positioned and supported in the middle section of the stepped spindle 15, limiting axial movement and bearing the primary load of the stepped spindle 15, preventing excessive deflection. The bearing seat a142 is bolted to the test bench base 10, providing support for the two deep groove ball bearings a141 on the stepped spindle 15. The sleeve 144 secures the deep groove ball bearings a141 axially. The servo motor a12 transmits torque to the stepped main shaft 15 through the coupling a13, thereby driving the inner ring of the intermediate bearing to rotate. The upper surface and lower surface of the motor base 11 are respectively connected to the servo motor a12 and the test bench base 10 by fastening bolts.

[0056] Combine Figure 4The outer ring drive system 2 consists of a servo motor b21, coupling b22, motor bracket 23, flange 24, gear shaft 25, driving bevel gear 26, deep groove ball bearing b27, bearing sleeve 28, bearing seat b29, and gland b30. Flange 24 and housing 92 are secured together using notches to secure bearing seat b29. The output shaft of servo motor b21 is connected to coupling b22, which transmits torque to gear shaft 25. Gear shaft 25 drives a pair of bevel gears, rotating intermediate bearing sleeve 524. The driven bevel gear 523 is welded to intermediate bearing sleeve 524, which is then transitionally fitted to the outer ring of the intermediate bearing, thereby driving the outer ring of intermediate bearing 32 to rotate.

[0057] Combine Figure 5 The intermediate bearing system 3 is composed of an eccentric disc 31, an intermediate bearing 32, and a hydraulic cover 33. The hydraulic cover 33 is fixedly connected to the intermediate bearing 32 by bolts. The inner ring of the intermediate bearing 32 is pressed against the hydraulic cover 33 to prevent the tested bearing from falling off or moving to the right. The eccentric disc 31 is stuck in the designated groove on the intermediate bearing sleeve 524. As the intermediate bearing sleeve 524 rotates, the centrifugal load is transmitted to the intermediate bearing 32 to simulate the working environment of the intermediate bearing 32. The left side of the inner ring of the intermediate bearing 32 is positioned by the shoulder of the stepped main shaft 15, and an interference fit is achieved with it in the form of a basic hole system. The high preload stiffness is used to avoid excessive stress deformation of the main shaft-inner ring due to instantaneous overload during the bearing test.

[0058] Referring to Figure 6(a), the oil injection system 4 consists of a side spray pipe 41 under the ring, a pipe cover 42, a lower oil collecting ring 43 under the ring, and a locking nut 44. The side spray pipe 41 under the ring is welded to the left end cover 91 of the housing. The locking nut 44 axially secures the lower oil collecting ring 43 under the ring. The side spray nozzle sprays oil toward the rotating element of the intermediate bearing 32 for lubrication. Under the ring, the lubricating oil flows through the oil groove at the bottom of the lower oil collecting ring 43 and enters the oil inlet hole at the bottom of the intermediate bearing 32, where it is then delivered into the interior of the intermediate bearing 32.

[0059] In conjunction with Figure 6 (b), when the pipe covers 42 of the lower ring spray pipes are all opened, the lubricating oil jet sprayed from the lubricating nozzles of the lower ring spray pipes is sprayed to the oil collecting groove of the lower ring oil collecting ring 43 through the air field in the bearing cavity. The lubricating oil enters the oil collecting channel of the lower ring oil collecting ring 43 through the oil collecting inlet and flows along the inner surface of the oil collecting blade. After flowing through the blade protrusions on the oil collecting blades, it enters the front oil collecting ring groove and then enters the bearing interior through the double oil inlet that passes through the bottom of the inner ring of the intermediate bearing.

[0060] Referring to Figure 7(a), the oil return system 5 consists of a left-side oil return system 51, a right-side oil return system 52, an oil chip sensor 53, and a flow sensor 54. The right-side oil return system 52 consists of a temperature sensor pipe 521, an oil retaining ring 522, a driven bevel gear 523, an intermediate bearing sleeve 524, a through-hole pneumatic slip ring 525, an oil return pipe 526, and a spiral U-groove 527. The left-side oil return system 51 is located to the left of the intermediate bearing 32. Its oil leakage pipe is embedded in the bottom of the housing and extends from the left end cover 91 of the housing to collect lubricating oil that rebounds from the left side of the intermediate bearing. The right-side oil return system 52 is located to the right of the intermediate bearing 32 and collects lubricating oil ejected from the right side of the intermediate bearing.

[0061] Referring to Figures 7(b)-7(d), the spiral U-groove 527 is embedded within the intermediate bearing sleeve 524. The opening of the spiral U-groove 527 receives the lubricating oil ejected from the right side of the intermediate bearing 32, and the distal end connects to the inlet of the oil return pipe 526, thereby introducing the lubricating oil into the oil return pipe 526. The through-hole pneumatic slip ring 525 is fixedly mounted in a designated groove within the intermediate bearing sleeve 524. The right side of the through-hole pneumatic slip ring 525 maintains a certain distance from the driven bevel gear 523 to ensure proper operation. The rotating end of the through-hole pneumatic slip ring 525 is connected to the right oil return pipe, while the stationary end is connected to the right oil leakage pipe. The oil retaining ring 522 is located in close proximity to the oil return pipe 526, thereby concentrating the lubricating oil ejected from the right side into the oil return pipe 526 below. The oil chip sensor 53 and the flow sensor 54 are both installed on the left and right oil leakage pipes. The flow sensor 54 is connected first, and then the oil chip sensor 53 is connected. Only the front sensing part of the flow sensor 54 is located in the oil leakage pipe, and all the lubricating oil in the oil leakage pipe passes through the oil chip sensor 53 and then flows out of the oil leakage pipe, which is used to measure the flow and wear conditions on the left and right sides of the intermediate bearing.

[0062] Combine Figure 8 The temperature measurement system 6 consists of a left-side temperature sensor 61 and a right-side temperature sensor 62. The temperature sensor pipe 521 has a vertical through-hole extending through the right temperature sensor and a horizontal through-hole extending through the left temperature sensor. The through-hole gas-electric slip ring 525 connects to the internal data lines of the left and right temperature sensors at its rotating end and to the external data line at its stationary end, outputting temperature data from both sides. The two temperature sensors collect temperature comparison data from the left and right outer rings of the intermediate bearing 32.

[0063] Combine Figure 9The tested bearing sleeve support system 7 consists of a deep groove ball bearing 71, a support bearing seat 72, and a hydraulic cover b73. The support bearing 71 and the tested bearing sleeve 524 employ a basic hole system with an interference fit. The support bearing seat 72 is bolted to the housing 9, and the support bearing seat 72 is also bolted to the housing 92. The internally buckled hydraulic cover b73 is bolted to the support bearing seat 72. The hydraulic cover b73 compresses the outer ring of the intermediate bearing 32 to prevent it from falling out or moving.

[0064] Combine Figure 10 The observation system 8 consists of a coaxial light source 81, a CCD high-speed camera 82, and an observation base 83. The base 83 is bolted to the T-shaped workbench 10; the coaxial light source 81 and the CCD high-speed camera 82 are also bolted to the base 83. The coaxial light source focuses the divergent light, while the CCD high-speed camera captures images of the bearing lubrication condition during operation.

[0065] Combine Figure 11 The housing 9 is composed of a left end cover 91, a shell 92, and a right glass end cover 93. The left end cover 91 and shell 92 are bolted together, the right glass end cover 93 and shell 92 are bolted together, and the shell 92 is bolted to the test bench base 10. A hole is drilled through the upper portion of the left end cover to transport lubricating oil. The shell 92 adopts an upper and lower split structure that facilitates installation and disassembly. The intermediate bearing system 3, oil return system 5, temperature measurement system 6, and intermediate bearing sleeve support system 7 are all installed inside the housing 9. The right glass end cover 93 facilitates clear observation of the movement of lubricating oil between the contact surfaces of the tested bearing under different lubrication conditions and different operating conditions.

[0066] The descriptions of the exemplary embodiments presented above are intended only to illustrate the technical solutions of the present invention and are not intended to be exhaustive or to limit the present invention to the precise forms described. Obviously, many changes and variations are possible for those skilled in the art based on the above teachings. The exemplary embodiments have been selected and described to explain the specific principles of the present invention and its practical applications, thereby making it easier for others skilled in the art to understand, implement, and utilize the various exemplary embodiments of the present invention and its various alternative forms and modifications.

Claims

1. A test device for observing the lubrication performance of an intermediate bearing lubrication structure under rotation of inner and outer rings, characterized in that: The lubrication performance observation test device of the intermediate bearing lubrication structure under the rotation of the inner and outer rings comprises an inner ring drive system (1), an outer ring drive system (2), an intermediate bearing system (3), an oil injection system (4), an oil return system (5), a temperature measurement system (6), an intermediate bearing sleeve support system (7), an observation system (8), a box (9) and a test bench base (10); the inner ring drive system (1), the box (9) and the observation system (8) are sequentially installed on the test bench base (10); The box body (9) includes a left end cover (91) of the box body, a shell (92) and a right glass end cover (93) of the box body; the shell (92) is a split structure, which is installed on the test bench base (10), and its two ends are respectively connected to the left end cover (91) of the box body and the right glass end cover (93) of the box body; the intermediate bearing system (3), the oil return system (5), the temperature measurement system (6), and the intermediate bearing sleeve support system (7) are all installed inside the box body (9); a notch is provided at the top of the shell body (92) for fixing the outer ring drive system (2); a through hole is drilled on the upper part of the left end cover (91) of the box body for connecting the oil injection system (4) to transport lubricating oil; the right glass end cover (93) of the box body is used to observe the motion state between the contact surfaces of the tested bearing of the shell body (92); The inner ring drive system (1) mainly consists of a motor base (11), a servo motor a (12), a coupling a (13), a support bearing seat system (14) and a stepped main shaft (15); one end of the stepped main shaft (15) is connected to the servo motor a (12) through the coupling a (13), and the other end is connected to the inner ring of the intermediate bearing (32); the support bearing seat system (14) is installed on the stepped main shaft (15), and the support bearing seat system (14) is fixed to the test bench base (10) through the T-type workbench; the servo motor a (12) is fixed to the test bench base (10) through the motor base (11); the servo motor a (12) transmits torque to the stepped main shaft (15) through the coupling a (13), thereby driving the inner ring of the intermediate bearing (32) to rotate Rotation; the supporting bearing seat system (14) includes a deep groove ball bearing a (141), a bearing seat a (142), a pressure cover a (143) and a sleeve (144); the bearing seat a (142) is sleeved on the stepped main shaft (15), and there is a gap between the two; the pressure cover a (143) is fixed at both ends of the bearing seat a (142); two deep groove ball bearings a (141) are installed in the gap between the bearing seat a (142) and the stepped main shaft (15) for positioning and supporting the stepped main shaft (15), limiting the axial movement of the stepped main shaft (15) and bearing the main load of the stepped main shaft (15) to prevent it from undergoing large deflection deformation; a sleeve (144) is installed between the two deep groove ball bearings a (141) on the stepped main shaft (15) for axially fixing the deep groove ball bearing a (141); The outer ring drive system (2) mainly consists of a servo motor b (21), a coupling b (22), a motor bracket (23), a flange (24), a gear shaft (25), an active bevel gear (26), a deep groove ball bearing b (27), a bearing sleeve (28), a bearing seat b (29) and a pressure cover b (30); the output shaft of the servo motor b (21) is connected to the coupling b (22), the gear shaft (25) and a pair of active bevel gears (26) in sequence; the active bevel gear (26) is meshed with the driven bevel gear (523) welded on the intermediate bearing sleeve (524), and the intermediate bearing sleeve (524) is located outside the outer ring of the intermediate bearing (32) and is transitionally matched with it; the gear shaft (25) is sleeved with a bearing Seat b (29), there is a gap between the two; the bearing seat b (29) and the pressure cover b (30) form a closed space; the bearing sleeve (28) and two deep groove ball bearings b (27) are sequentially installed in the closed space from the outside to the inside; the end of the bearing seat b (29) passes through the gap of the housing (92), and its side is fixed to the housing (92) through the flange (24); the servo motor b (21) is fixed to the housing (92) through the motor bracket (23); the servo motor b (21) transmits torque to the gear shaft (25) through the coupling b (22), and the gear shaft (25) drives the active bevel gear (26) to rotate, thereby rotating the intermediate bearing sleeve (524), and finally driving the outer ring of the intermediate bearing (32) to rotate; The intermediate bearing system (3) is mainly composed of an eccentric disk (31), an intermediate bearing (32) and a hydraulic cover (33); the inner side of the intermediate bearing (32) is fixedly connected to the hydraulic cover (33), and the hydraulic cover (33) presses the inner ring of the intermediate bearing (32) to prevent it from falling off and moving; the eccentric disk (31) is installed on the outer side of the intermediate bearing (32), and the eccentric disk (31) is clamped in a groove provided on the intermediate bearing sleeve (524). As the intermediate bearing sleeve (524) rotates, the centrifugal load is transmitted to the intermediate bearing (32) to simulate the working environment of the intermediate bearing (32); The oil injection system (4) mainly consists of a lower ring side spray pipe (41), a pipe cover (42), a lower ring oil collecting ring (43) and a locking nut (44); the lower ring side spray pipe (41) is welded to the left end cover (91) of the box body and is connected to the through hole of the left end cover (91) of the box body; the lower ring side spray pipe (41) includes a lower ring pipe and a side spray pipe, and a lubrication nozzle with a pipe cover (42) is provided at one end of the two pipes; the lower ring oil collecting ring (43) is fixed to the outside of the stepped main shaft (15) through the locking nut (44), the lubrication nozzle of the lower ring pipe is located above the lower ring oil collecting ring (43), and the oil groove of the lower ring oil collecting ring (43) is connected to the oil inlet hole at the bottom of the intermediate bearing (32) through the stepped main shaft (15); the lubrication nozzle of the side spray pipe is located on the side of the rotating body of the intermediate bearing (32); The oil return system (5) is mainly composed of a left oil return system (51), a right oil return system (52), an oil chip sensor (53) and a flow sensor (54); the left oil return system (51) is located on one side of the intermediate bearing (32), and its left oil leakage pipe is embedded in the bottom of the box (9) and extends from the left end cover (91) of the box to collect the lubricating oil rebounded from one side of the intermediate bearing (32); the right oil return system (52) is located on the other side of the intermediate bearing (32) and is used to collect the lubricating oil rebounded from the intermediate bearing (32). The lubricating oil is ejected from the other side of the bearing (32); the right oil return system (52) includes a temperature sensor pipe (521), an oil retaining ring (522), a driven bevel gear (523), an intermediate bearing sleeve (524), a through-hole gas-electric slip ring (525), an oil return pipe (526) and a spiral U-groove (527); the spiral U-groove (527) is embedded in the intermediate bearing sleeve (524), one end of which receives the lubricating oil ejected from the other side of the intermediate bearing (32), and the other end is connected in sequence to The oil return pipe (526) and the rotating end of the through-hole gas-electric slip ring (525), the through-hole gas-electric slip ring (525) is fixed on the outside of the intermediate bearing sleeve (524), and there is a gap between the through-hole gas-electric slip ring (523) and the driven bevel gear (523), so as to ensure the normal operation of the driven bevel gear (523); the stationary end of the through-hole gas-electric slip ring (525) is connected to the right oil leakage pipe; the right oil leakage pipe is embedded in the bottom of the box (9) and extends out from the right glass end cover (93) of the box; the oil retaining ring (522) is fixed to the intermediate bearing The inner side of the sleeve (524) is located on one side of the oil return pipe (526), blocking the lubricating oil ejected from the other side of the intermediate bearing (32), so that the lubricating oil is concentrated in the oil return pipe (526) below; a flow sensor (54) and an oil chip sensor (53) are arranged in sequence on the oil leakage pipe to measure the lubricating oil flow and wear conditions on both sides of the intermediate bearing (32); a temperature sensor pipe (521) is arranged in the wall of the intermediate bearing sleeve (524), which includes a vertical through hole and a horizontal hole; The temperature measurement system (6) includes a left temperature sensor (61) and a right temperature sensor (62); one end of the left temperature sensor (61) is connected to one side of the outer ring of the intermediate bearing (32), and the other end is connected to the rotating end of the through-hole gas-electric slip ring (525) through the horizontal hole of the temperature sensor pipe (521); one end of the right temperature sensor (62) is connected to the other side of the outer ring of the intermediate bearing (32), and the other end is connected to the rotating end of the through-hole gas-electric slip ring (525) through the vertical through hole of the temperature sensor pipe (521); the left temperature sensor (61) and the right temperature sensor (62) respectively collect temperature comparison data on both sides of the outer ring of the intermediate bearing (32); the static end of the through-hole gas-electric slip ring (525) is connected to the external data line to output the temperature; The tested bearing sleeve support system (7) includes a deep groove ball support bearing (71), a support bearing seat (72) and a hydraulic cover b (73); the deep groove ball support bearing (71) and the intermediate bearing sleeve (524) are interference fit in a base hole system; the support bearing seat (72) is sleeved outside the deep groove ball support bearing (71) and fixedly connected to the housing (9); the hydraulic cover b (73) is fixed between the support bearing seat (72) and the deep groove ball support bearing (71), and the hydraulic cover b (73) presses the intermediate bearing sleeve (524) inside, thereby preventing the outer ring of the intermediate bearing (32) from falling off and moving; The observation system (8) includes a coaxial light source (81), a CCD high-speed camera (82) and an observation base (83); the observation base (83) is connected to the test bench base (10) through a "J"-shaped workbench; the coaxial light source (81) and the CCD high-speed camera (82) are fixed on the observation base (83) in sequence; the coaxial light source (81) gathers the divergent light, and the CCD high-speed camera (82) realizes the image acquisition of the lubrication condition of the measured bearing during the working process.

2. The lubrication performance observation test device for the intermediate bearing lubrication structure with inner and outer rings rotating according to claim 1, characterized in that: The test bench base (10) is provided with multiple tracks, and the inner ring drive system (1), the box (9) and the observation system (8) are fixed after moving on the tracks.

3. The lubrication performance observation test device for the intermediate bearing lubrication structure with inner and outer rings rotating according to claim 1 or 2, characterized in that: One side of the inner ring of the intermediate bearing (32) is positioned by the shoulder of the stepped main shaft (15), and the shoulder and the inner ring of the intermediate bearing (32) are interference-fitted in a hole-based manner, and the preload stiffness is set to avoid large stress deformation between the main shaft and the inner ring due to instantaneous overload during the bearing test.

4. The lubrication performance observation test device for the intermediate bearing lubrication structure with inner and outer rings rotating according to claim 3, characterized in that: Only the front sensing portion of the flow sensor (54) is located in the oil leakage pipeline; all the lubricating oil in the oil leakage pipeline flows out of the oil leakage pipeline through the oil chip sensor (53).

5. A test method for observing the lubrication performance of the intermediate bearing lubrication structure under the rotation of the inner and outer rings according to any one of claims 1 to 4, characterized in that: The steps are as follows: Step 1: Start the servo motor a (12) and the servo motor b (21) to respectively drive the rotation of the stepped main shaft (15) and the gear shaft (25), so that the inner ring and the outer ring of the intermediate bearing (32) rotate synchronously; apply an eccentric load to the intermediate bearing (32) through the eccentric disk (31) located on the bearing sleeve (524) to simulate the working environment; Step 2, by controlling the opening and closing of the pipe covers (42) at the under-ring pipe and the side spray pipe, and simultaneously cooperating with the left oil return system (51), the right oil return system (52), the flow sensor (54) and the oil chip sensor (53) on both sides of the intermediate bearing (32), the return oil flow and wear characteristics on the left and right sides of the intermediate bearing (32) are monitored, and a comparative analysis is achieved on the supply of flow on both sides of the intermediate bearing (32) under three conditions: only under-ring lubrication, only side spray lubrication, and simultaneous under-ring and side spray lubrication; Step 3: The through-hole gas-electric slip ring (525) is connected to a left temperature sensor (61) and a right temperature sensor (62) for monitoring the temperatures of the left and right sides of the outer ring of the intermediate bearing (32). The rotating end of the through-hole gas-electric slip ring (525) rotates together with the intermediate bearing (32), and the stationary end outputs temperature data to collect the temperatures of the left and right sides of the outer ring of the intermediate bearing (32) during the lubrication process. Step 4: Change the lubrication parameters, monitor the return oil flow and wear on the left and right sides of the intermediate bearing (32) and the temperature on the left and right sides of the outer ring under different lubrication conditions; and establish the relationship between the flow field characteristics, temperature characteristics, and wear characteristics of the intermediate bearing (32).

6. The test method according to claim 5, characterized in that The lubrication parameters include the flow rate of the lubrication nozzle and the angle of the lubrication nozzle.

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