CN219038372U

CN219038372U - Hydraulic loading system of roller bearing and guide wheel coating performance test device

Info

Publication number: CN219038372U
Application number: CN202223436864.7U
Authority: CN
Inventors: 徐建波
Original assignee: Hangzhou Dishichuan Intelligent Equipment Co ltd
Current assignee: Hangzhou Dishichuan Intelligent Equipment Co ltd
Priority date: 2022-12-21
Filing date: 2022-12-21
Publication date: 2023-05-16
Anticipated expiration: 2032-12-21

Abstract

The utility model discloses a hydraulic loading system of a roller bearing and guide wheel coating performance test device. The hydraulic loading system comprises a hydraulic oil tank, a plunger pump, a servo motor and a hydraulic oil way, wherein an overflow valve, a digital servo valve and an electromagnetic reversing valve are sequentially arranged on the hydraulic oil way from the plunger pump to the direction of the hydraulic cylinder. The hydraulic loading system with the structure is provided with two groups which are respectively and independently controlled and are connected with the two hydraulic cylinders of the pair of loading components, so that the independence and the reliability of loading of the two groups of loading components from two directions are ensured. In the loading process, the lower computer controller achieves the effects of force adding/subtracting and force maintaining by controlling the rotating speed of the servo motor, and the servo motor and the plunger pump dynamically supplement pressure to the hydraulic oil way in real time without full power operation because the servo motor has accurate control capability, so the hydraulic loading system has the technical advantages of high loading precision, low working noise, low maintenance cost, energy conservation, environmental protection and the like.

Description

Hydraulic loading system of roller bearing and guide wheel coating performance test device

Technical Field

The utility model relates to the technical field of life test of a roller bearing outer ring under a rotating working condition, in particular to a hydraulic loading system of a roller bearing and guide wheel coating performance test device.

Background

The application working condition of the aircraft body roller bearing is complex, and the requirement on the service life is far higher than that of a conventional roller bearing under the outer ring rotating working condition. In the testing link of the aircraft body roller bearing, the running state of forward and reverse rotation of the roller bearing and the service life under different loading conditions need to be simulated. However, the conventional bearing life tester is difficult to meet the test working conditions of the aircraft body roller bearing.

Therefore, it is necessary to design a test device applied to the aircraft body roller bearing, which can simulate the running state of the forward and reverse rotation of the roller bearing, different loading conditions of the roller bearing and the service life of the roller bearing under different loading conditions; and the friction and wear life of the coating on the dual guide wheel can be tested by taking the roller bearing as a carrier and through the change conditions of the friction coefficient and the wear amount.

In the test device applied to the aircraft body roller bearing, the precise control of the load bearing force is particularly important, and the application aims to provide a hydraulic loading system with precise load control so as to improve the reliability of the life test of the roller bearing.

Disclosure of Invention

The utility model aims to solve the technical problem of providing a hydraulic loading system which can be applied to a roller bearing and guide wheel coating performance test device for an aircraft body roller bearing test so as to realize accurate control of bearing load.

In order to solve the technical problems, the technical scheme provided by the utility model is as follows: the hydraulic loading system of the roller bearing and guide wheel coating performance test device at least comprises:

a base;

the guide wheel assembly at least comprises a guide wheel and a driving mechanism for driving the guide wheel to rotate;

the loading part is symmetrically arranged at two sides of the guide wheel assembly and at least comprises a fixed loading seat, a movable loading seat capable of moving towards the guide wheel assembly side in a bidirectional way relative to the fixed loading seat and a loading driving part for driving the movable loading seat to move;

the bearing test unit comprises a test bearing seat for installing a test bearing, and the test bearing seat is arranged on one side of the movable loading seat, which faces the opposite rolling guide wheel; and

the wear measuring component is arranged between the fixed loading seat and the movable loading seat;

the loading driving component is a hydraulic cylinder, two hydraulic cylinders are provided with hydraulic loading systems which are respectively and independently controlled, and the hydraulic loading systems at least comprise:

the hydraulic oil tank is used for storing hydraulic oil;

the plunger pump is arranged in the hydraulic oil tank;

the servo motor is connected with the plunger pump and drives the plunger pump;

the hydraulic oil way is connected with the plunger pump and the hydraulic cylinder, and an overflow valve, a digital servo valve and a reversing valve are sequentially arranged on the hydraulic oil way from the plunger pump to the hydraulic cylinder;

the pressure gauge is arranged on the hydraulic oil path and used for monitoring the oil pressure of the system; and

and the pressure sensor is used for monitoring the oil pressure in the working cavity of the hydraulic cylinder.

In a preferred embodiment, the reversing valve is an electromagnetic reversing valve.

In a preferred embodiment, a fine filter is arranged on the hydraulic oil path between the plunger pump and the overflow valve.

The hydraulic loading system of the roller bearing and guide wheel coating performance test device has the following beneficial effects:

(1) The hydraulic loading systems of the two hydraulic cylinder configurations of the pair of loading components are independently controlled, so that the independence and reliability of loading of the two groups of loading components from two directions are ensured.

(2) In the loading process of the hydraulic loading system, the lower computer controller achieves the effects of force loading/unloading and force holding by controlling the rotating speed of the servo motor, and the servo motor and the plunger pump dynamically supplement pressure to the hydraulic oil way in real time without full power operation because the servo motor has accurate control capability, so the hydraulic loading system has the technical advantages of high loading precision, low working noise, low maintenance cost, energy conservation, environmental protection and the like.

Drawings

FIG. 1 is a schematic diagram of a roller bearing and guide wheel coating performance test apparatus according to the present embodiment;

FIG. 2 is a side view of the idler assembly of the present embodiment;

FIG. 3 is a schematic cross-sectional structural view of the idler assembly of FIG. 2;

FIG. 4 is a schematic view of a perspective state structure of the idler assembly of FIG. 2;

FIG. 5 is a schematic view of an exploded view of a guide wheel and a guide wheel base of the guide wheel assembly of FIG. 2;

FIG. 6 is a schematic view of a guide wheel and guide wheel shaft assembly of the guide wheel assembly of FIG. 2;

FIG. 7 is a schematic cross-sectional view of the structure of FIG. 6;

FIG. 8 is a schematic view showing a three-dimensional structure of the loading unit according to the present embodiment;

FIG. 9 is a schematic diagram showing a front view of the loading unit according to the present embodiment;

fig. 10 is a schematic structural view of a bearing test unit according to the first embodiment of the present embodiment, in which the test bearing is a sealed bearing;

FIG. 11 is a schematic view of an exploded view of the bearing test unit of FIG. 10;

FIG. 12 is a schematic cross-sectional structural view of the bearing test unit of FIG. 10;

fig. 13 is a schematic structural view of a bearing test unit according to a second embodiment of the present embodiment, in which the test bearing is a non-sealing bearing;

FIG. 14 is a schematic view of an exploded view of the bearing test unit of FIG. 13;

FIG. 15 is a schematic cross-sectional structural view of the bearing test unit of FIG. 13;

FIG. 16 is a schematic view of the spacer ring of the bearing test unit of FIG. 13;

fig. 17 is a schematic diagram of the hydraulic loading system in the present embodiment.

Detailed Description

The present utility model will be described in further detail with reference to the drawings and examples, in order to make the objects, technical solutions and advantages of the present utility model more apparent. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the scope of the utility model.

In the description of the present utility model, it should be understood that the directions or positional relationships indicated by the terms "upper", "lower", "front", "rear", "inner", "outer", etc., are based on the directions or positional relationships shown in the drawings, are merely for convenience of describing the present utility model and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the present utility model.

In the description of the present utility model, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, integrally connected, or detachably connected; may be a communication between the interiors of two elements; may be directly or indirectly through an intermediate medium, and the specific meaning of the terms in the present utility model will be understood by those skilled in the art in specific cases.

The roller bearing and guide wheel coating performance test device of the embodiment, as shown in fig. 1, comprises a base 40 fixedly arranged, a guide wheel assembly 10 fixedly arranged on the base 40, loading components 30 arranged on two sides of the guide wheel assembly, and a bearing test unit 20 arranged on the loading components 30.

In this embodiment, the structure of the guide wheel assembly 10 is shown in fig. 2-7, and includes a guide wheel 11 and a driving mechanism for driving the guide wheel to rotate, where the guide wheel 11 is mounted on a guide wheel base 14, and the guide wheel base 14 is fixedly mounted on the base 40. Preferably, in this embodiment, idler base 14 is fixedly coupled to base 40 by bolts.

In this embodiment, the guide wheel base 14 includes a fixing base 141 fixedly connected to the base 40, a pair of support arms 142 are disposed on the fixing base 141, and a guide wheel cavity 140 for accommodating the guide wheel 11 is formed between the support arms 142.

In this embodiment, the support arm 142 further includes a pressing cover 143 fixedly connected to an upper end of the support arm 142, and preferably, in this embodiment, the pressing cover 143 is fixedly connected to the support arm 142 through a bolt. Wherein a bearing mounting cavity 144 for receiving a support bearing is provided between the gland 143 and the arm 142.

In this embodiment, the guide wheel 11 is sleeved on the guide wheel shaft 11, the end portion of the guide wheel shaft 11 is provided with a polygonal connecting shaft hole 110, and the guide wheel shafts 11 on two sides of the guide wheel are sequentially provided with a first spacer 113 adjacent to the guide wheel 11, a support bearing 114 adjacent to the first spacer 113, and a locking sleeve 115 adjacent to the support bearing 114 and fixedly connected with the end portion of the guide wheel shaft 111. Preferably, in this embodiment, the locking sleeve 115 is screwed to the end of the guide shaft 111.

In this embodiment, first, the guide wheel 11, the guide wheel shaft 11, the two first spacers 113, the two support bearings 114 and the two locking sleeves 115 are assembled into the assembly structure shown in fig. 6-7, and as shown in fig. 5, the assembly structure is placed on the fixing seat 141, and the gland 143 is connected to the support arm 142 through the bolt, wherein the support bearings 114 are located in the bearing installation cavity 144.

Further, in this embodiment, the guide wheel further includes a fixing ring 145 disposed on the outer side of the support arm 142, where the fixing ring 145 is fixedly connected with the gland 143 and the outer side surface of the support arm 142 through bolts, so that the guide wheel is more reliable to install and has better structural stability.

In this embodiment, the driving mechanism for driving the guide wheel 11 to rotate, as shown in fig. 2-4, includes a servo motor 12, a speed reducer 121 connected to an output end of the servo motor 12, an output shaft 112 connected to the guide wheel shaft 11, and a coupling 13 connecting an output end of the speed reducer 121 and the output shaft 112.

As a feature of the present embodiment, a torque sensor 122 is provided between the couplings 13, and in the present embodiment, a driver (not shown) and a measurement and control system (not shown) are provided, which controls the servo motor to change speed steplessly and rotate forward and backward by the driver, and monitors the friction torque by the torque sensor.

Preferably, in this embodiment, the torque sensor 122 is mounted on the bracket 16, and the bracket 16 is fixedly connected to the base 40.

Preferably, in the present embodiment, the servo motor 12 and the speed reducer 121 are mounted on a motor bracket 15, and the motor bracket 15 is fixedly connected to the base 40.

In this embodiment, a pair of loading members 30 are symmetrically installed on both sides of the guide wheel assembly 10, as shown in fig. 8 and 9, the loading members include a fixed loading seat 33, a movable loading seat 34 capable of moving bi-directionally relative to the fixed loading seat 33 toward the guide wheel assembly, and a loading driving member 31 for driving the movable loading seat 34 to move.

In this embodiment, a pair of fixed loading bases 33 are disposed opposite to each other and fixedly mounted on the base 40, and 4 sets of guiding mechanisms are disposed between the fixed loading bases 33 and the movable loading bases 34. The guiding mechanism comprises a guiding rod 35 and a guiding sleeve 36 which is connected with the guiding rod in an adapting way. As a special feature of this embodiment, two ends of the guide rod 35 are fixedly connected to a pair of fixed loading bases 33, and four guide sleeves 36 are disposed on the movable loading bases 34 and are respectively sleeved on the guide rod 35. A pair of movable load seats 34 are disposed between a pair of fixed load seats 33.

In this embodiment, since the two ends of the guide rod are fixedly connected to the pair of fixed loading bases 33, and the two movable loading bases 34 move based on the guide rods with the same reference, the accuracy of the loading force applied by the two sets of loading components 30 is particularly high, and for the test bearings or the paired rolling guide wheels, the higher the accuracy of the loading force applied, the more reliable the test result.

In this embodiment, the loading driving component 31 is fixedly connected to the outer side of the fixed loading seat 33, and the telescopic rod 32 passes through the fixed loading seat 33 and is fixedly connected to the movable loading seat 34.

In this embodiment, the loading driving component 31 is a hydraulic cylinder, and as shown in fig. 17, two hydraulic cylinders are configured with hydraulic loading systems that are controlled independently, so that the independence and reliability of loading of the two groups of loading components from two directions are ensured.

In this embodiment, the hydraulic loading system at least includes a hydraulic oil tank for storing hydraulic oil, a plunger pump disposed in the hydraulic oil tank, a servo motor connected to the plunger pump and used for driving the plunger pump, and a hydraulic oil path. The hydraulic oil way is used for connecting the plunger pump and the hydraulic cylinder, and the hydraulic oil in the hydraulic oil tank is conveyed into the working cavity of the hydraulic cylinder.

In this embodiment, an overflow valve, a digital servo valve and an electromagnetic directional valve are sequentially disposed on the hydraulic oil path from the plunger pump to the hydraulic cylinder. Wherein, the overflow valve controls the pressure and the opening of the digital servo valve; the electromagnetic reversing valve plays a role in reversing hydraulic oil and is mainly used for controlling loading and unloading of the hydraulic cylinder. The hydraulic oil circuit is also provided with a pressure gauge and an oil pressure sensor which are respectively used for monitoring the system oil pressure and the oil pressure in the working cavity of the oil cylinder.

Preferably, in this embodiment, a fine filter is disposed on the hydraulic oil path between the plunger pump and the relief valve, and is used for fine filtering the hydraulic oil.

In the hydraulic loading system of the embodiment, in the loading process, the lower computer controller controls the rotating speed of the servo motor to achieve the effects of force loading/unloading and force holding. Because the servo motor has accurate control capability, and the servo motor and the plunger pump dynamically supplement pressure to the hydraulic oil way in real time, full-power operation is not needed, the hydraulic loading system has the advantages of high loading precision, low working noise, low maintenance cost, energy conservation, environmental protection and the like.

The test bearing 21 to be tested is lubricated by having two types, one being a sealed bearing based on grease stored therein. The other is a non-sealing bearing, and lubrication is needed by lubricating oil in the working process. Based on the above-mentioned different types of test bearings, the test apparatus of this embodiment is also adapted.

The bearing test unit 20 of the first embodiment of the present embodiment is applied to a sealed bearing. As shown in fig. 10-12, the test bearing seat comprises a base 22, a pair of pressing seats 25 which are connected with the base in an adapting way, and a test shaft 26, wherein the base 22 is arranged on the side of the movable loading seat 34 facing the guide wheel. The base 22 is provided with a receiving section 23 for receiving the test bearing 21, a pair of pressing seats 25 are positioned on two sides of the receiving section 23, and a shaft cavity 24 for installing a test shaft 26 is arranged between the pressing seats 25 and the base 22.

In this embodiment, the position of the test shaft 26 near one end is provided with a shaft shoulder 27, and further includes a second spacer bush 28 sleeved on the test shaft, where the test bearing 21 is mounted on the test shaft 26 between the shaft shoulder 27 and the second spacer bush 28, and the outer sides of the shaft shoulder 27 and the second spacer bush 28 are abutted against the inner wall of the accommodating section 23 and the inner wall of the pressing seat 25, so that the test bearing 21 is mounted on the test bearing seat.

In this embodiment, the loading component drives the test bearing to move until the outer surface of the test bearing contacts with the outer surface of the guide wheel, and the driving mechanism drives the guide wheel to rotate, so as to drive the outer ring of the test bearing to rotate. The measurement and control system controls stepless speed change and forward and reverse rotation of the servo motor through the driver, and the loading force applied by the loading component is also adjustable, so that the service life of the test bearing under different working conditions is simulated, and the working conditions comprise forward and reverse rotation, different speeds, different loading conditions and the like.

The bearing test unit 20 of the second embodiment of the present utility model is applied to a non-sealed bearing. As shown in fig. 14-16, the bearing test unit 20 further includes a sealing sleeve 211 sleeved on the outer side of the test bearing and sealing covers 212 fixedly connected with two ends of the sealing sleeve 211, the two sealing covers 212 are sleeved on the outer sides of the shaft shoulder 27 and the second spacer bush 28 respectively, and a sealing ring 213 is arranged between the sealing cover and the shaft shoulder 27 and between the sealing cover and the second spacer bush 28, so that after the arrangement, a relatively sealed space is formed by the sealing sleeve 211, the two sealing covers 212, the shaft shoulder 27 and the second spacer bush 28.

In order to realize the lubrication of the non-sealing test bearing, in this embodiment, as shown in fig. 15, one end of the test shaft 26 is provided with a lubricant oil inlet channel which is communicated with the inner side of the sealing sleeve, and the lubricant oil inlet channel comprises an axial oil inlet channel 261 and a radial oil inlet channel 262. The other end of the test shaft 26 is provided with a lubricant outlet passage communicating with the inside of the sealing sleeve, and the lubricant outlet passage includes an axial oil outlet passage 263 and a radial oil outlet passage 264. Wherein, radial oil inlet passage 262 can be provided in plurality around axial oil inlet passage 261, and radial oil outlet passage 264 can be provided in plurality around axial oil outlet passage 263.

Preferably, in the present embodiment, two non-sealing test bearings 21 are provided side by side. The inner ring of the test bearing 21 is in interference fit connection with the test shaft 26, and the outer ring of the test bearing 21 is in interference fit connection with the sealing sleeve 211.

Correspondingly, in the present embodiment, a spacer ring 29 sleeved on the test shaft 26 is disposed between the inner rings of the two test bearings 21. Preferably, the inner ring of the spacer ring 29 is provided with an oil groove 291, and the spacer ring 29 is further provided with a plurality of oil holes 292 penetrating to the oil groove 291 in the circumferential direction. Wherein, radial oil inlet passage 262 communicates to oil groove 291, radial oil outlet passage 264 communicates to the outside space of the test bearing.

In this embodiment, the lubricating oil system introduces lubricating oil into the axial oil inlet channel 261, and the lubricating oil flows from the axial oil inlet channel 261 to the lubricating oil system sequentially through the radial oil inlet channel 262, the oil groove 291, the oil hole 292 and the gaps between the inner ring and the outer ring of the test bearing, and then flows back to the lubricating oil system sequentially through the radial oil outlet channel 264 and the axial oil outlet channel 263, so as to form a circulating lubricating oil path.

In this embodiment, the loading part drives the test bearing unit to move until the outer surface of the sealing sleeve contacts with the outer surface of the guide wheel, and the driving mechanism drives the guide wheel to rotate, so that the outer ring of the test bearing is driven to rotate through the sealing sleeve. The measurement and control system controls stepless speed change and forward and reverse rotation of the servo motor through the driver, and the loading force applied by the loading component is also adjustable, so that the service life of the test bearing under different working conditions is simulated, and the working conditions comprise forward and reverse rotation, different speeds, different loading conditions and the like.

As a feature of the present embodiment, as shown in fig. 1, 8, and 9, a wear measuring device 50 is further provided between the fixed load carrier 33 and the movable load carrier 34 for monitoring the change in the distance between the fixed load carrier 33 and the movable load carrier 34. It should be noted that, the wear measuring device 50 is a well-known technology, and is used for monitoring the change of the interval, i.e. the wear amount, and is purchased, and the specific structure thereof is not described in detail in this embodiment.

In this embodiment, the friction torque is measured by the torque sensor 122 by using the roller bearing (test bearing) as the carrier, and the friction coefficient is calculated by combining the friction torque with the parameters such as the bearing size, the load bearing capacity, etc., and the friction life of the sprayed coating on the guide wheel 11 as the mating member can be assessed and evaluated by combining the friction coefficient with the wear amount measured by the wear measuring part 50.

In summary, the foregoing description is only of the preferred embodiments of the utility model, and is not intended to limit the utility model to the particular embodiments disclosed, but on the contrary, the intention is to cover all modifications, equivalents, and alternatives falling within the spirit and scope of the utility model.

Claims

1. The hydraulic loading system of the roller bearing and guide wheel coating performance test device at least comprises:

a base;

the hydraulic loading system is characterized in that the loading driving component is a hydraulic cylinder, the two hydraulic cylinders are provided with hydraulic loading systems which are respectively and independently controlled, and the hydraulic loading systems at least comprise:

the hydraulic oil tank is used for storing hydraulic oil;

the plunger pump is arranged in the hydraulic oil tank;

the servo motor is connected with the plunger pump and drives the plunger pump;

2. The hydraulic loading system of claim 1, wherein the reversing valve is an electromagnetic reversing valve.

3. A hydraulic loading system according to claim 1 or 2, characterized in that a fine filter is arranged in the hydraulic oil circuit between the plunger pump and the overflow valve.