CN117074019A - experimental device - Google Patents

Abstract

The application discloses an experimental device. The experimental device comprises a driving assembly, a thrust bracket and a thrust assembly; the thrust assembly is located between the first thrust bearing and the second thrust bearing, and the thrust assembly comprises a first portion and a second portion which are arranged at intervals along the axial direction of the driving output shaft, wherein the first portion is used for being abutted to the shell of the first thrust bearing, and the second portion is used for being abutted to the shell of the second thrust bearing so as to apply a force to the shell of the first thrust bearing and the shell of the second thrust bearing, wherein the direction of the force is parallel to the axial direction of the driving output shaft. Therefore, torque can be applied to the first thrust bearing and the second thrust bearing through the driving motor, and acting force with the axial direction parallel to the axial direction of the driving output shaft can be applied to the first thrust bearing and the second thrust bearing through the thrust component, so that the thrust bearings can be tested more effectively; in addition, can test first thrust bearing and second thrust bearing simultaneously, test efficiency is high.

Description

Experimental device

Technical Field

The application relates to the field of ship experimental equipment, in particular to an experimental device.

Background

Thrust bearings are an important component of the marine propulsion shafting. The thrust bearing is used for transmitting the torque of the main engine, bearing the axial thrust of the propeller and transmitting the axial thrust to the ship body so as to push the ship to advance or retreat.

The field of ships often requires testing of thrust bearings. The existing experimental device for testing the thrust bearing can only test one thrust bearing in sequence, and has low testing efficiency.

To this end, the present application provides an experimental device to at least partially solve the above-mentioned problems.

Disclosure of Invention

In the summary, a series of concepts in simplified form are introduced, which will be further described in detail in the detailed description. The summary of the application is not intended to define the key features and essential features of the claimed subject matter, nor is it intended to be used as an aid in determining the scope of the claimed subject matter.

To at least partially solve the above technical problem, the present application provides an experimental apparatus for testing a thrust bearing, the thrust bearing including a first thrust bearing and a second thrust bearing, the thrust bearing having a thrust output shaft, the experimental apparatus including:

the driving output shaft of the driving assembly is used for being connected to one end of the thrust output shaft of the first thrust bearing;

the thrust bracket is fixedly arranged;

the thrust assembly is located between the first thrust bearing and the second thrust bearing along the axial direction of the driving output shaft, and comprises a first part and a second part which are arranged at intervals along the axial direction of the driving output shaft, wherein the first part is used for being abutted to the shell of the first thrust bearing, and the second part is used for being abutted to the shell of the second thrust bearing so as to apply acting force with the directions parallel to the axial direction of the driving output shaft to the shell of the first thrust bearing and the shell of the second thrust bearing respectively.

According to the experimental device disclosed by the application, the torque can be applied to the first thrust bearing and the second thrust bearing through the driving motor, and the acting force with the axial direction parallel to the axial direction of the driving output shaft can be applied to the first thrust bearing and the second thrust bearing through the thrust component, so that the thrust bearings can be tested more effectively; in addition, can test first thrust bearing and second thrust bearing simultaneously, test efficiency is high.

Optionally, the thrust assembly includes a first thrust assembly and a second thrust assembly, along a width direction of the thrust bracket, the first thrust assembly is located at one side of an axis of the driving output shaft, the second thrust assembly is located at the other side of the axis of the driving output shaft, a distance between the first thrust assembly and the axis of the driving output shaft, and a distance between the second thrust assembly and the axis of the driving output shaft are equal, and the width direction of the thrust bracket is perpendicular to an axial direction of the driving output shaft and a height direction of the thrust bracket.

Optionally, the thrust bracket is located between the first thrust bearing and the second thrust bearing in an axial direction of the drive output shaft.

Optionally, the thrust assembly comprises a thrust member and an elongate shaft, the thrust member being retractable along an axial direction of the drive output shaft, one end of the thrust member being connected to one end of the elongate shaft.

Optionally, the thrust member comprises a thrust cylinder, and/or

The thrust support has the arc mounting groove that the opening up, and the thrust subassembly sets up in the arc mounting groove.

Optionally, the thrust component further comprises a connecting sleeve and a fastener, the lengthening shaft comprises a large section and a small section with the diameter smaller than that of the large section, the large section is located at the end of the lengthening shaft, one end of the connecting sleeve is connected to the thrust component, the large section is arranged in the connecting sleeve, and the fastener penetrates through the peripheral wall of the connecting sleeve and extends between the peripheral surface of the large section and the peripheral surface of the small section.

Optionally, the experimental device further comprises a pressure sensor connected to one end of the thrust assembly in the axial direction of the drive output shaft for collecting the magnitude of the force.

Optionally, the experimental device comprises a radial loading assembly, one end of a radial loading shaft of the radial loading assembly is connected to the thrust output shaft, and the radial loading assembly is capable of applying a downward radial force to the radial loading shaft.

Optionally, the radial loading assembly comprises a first radial loading assembly and a second radial loading assembly, one end of the radial loading shaft of the first radial loading assembly is connected to the drive output shaft, the other end of the radial loading shaft of the first radial loading assembly is connected to the thrust output shaft of the first thrust bearing,

one end of the radial loading shaft of the second radial loading assembly is connected to an end of the second thrust bearing remote from the first thrust bearing.

Optionally, the experimental device further comprises a mounting seat and a roller, the mounting seat is provided with a connecting long hole with a long shaft parallel to the axial direction of the driving output shaft, the axial direction of the roller is parallel to the width direction of the thrust bracket, the roller is rotatably connected to the mounting seat, and the second thrust bearing is connected to the mounting seat through the connecting long hole and is lapped to the roller.

Optionally, the experimental device further comprises a first mount and a second mount, the first thrust bearing and the first radial loading assembly are both connected to the first mount, and the second thrust bearing and the second radial loading assembly are both connected to the second mount.

Drawings

In order that the advantages of the application will be readily understood, a more particular description of the application briefly described above will be rendered by reference to specific embodiments that are illustrated in the appended drawings. Understanding that these drawings depict only typical embodiments of the application and are not therefore to be considered to be limiting of its scope, the application will be described and explained with additional specificity and detail through the use of the accompanying drawings.

FIG. 1 is a schematic front view of an experimental setup according to a preferred embodiment of the application;

FIG. 2 is a schematic top view of the experimental setup of FIG. 1;

FIG. 3 is a schematic front view of the thrust assembly and pressure sensor of the experimental set-up of FIG. 1 coupled together;

FIG. 4 is a schematic perspective view of a radial loading assembly of the experimental setup of FIG. 1;

FIG. 5 is a schematic perspective view of a second mount of the experimental setup of FIG. 1; and

fig. 6 is a schematic diagram of a hydraulic assembly of the experimental setup of fig. 1.

Detailed Description

In the following description, numerous specific details are set forth in order to provide a more thorough understanding of the present application. It will be apparent, however, to one skilled in the art that embodiments of the application may be practiced without one or more of these details. In other instances, well-known features have not been described in detail in order to avoid obscuring the embodiments of the application.

Preferred embodiments of the present application will be described below with reference to the accompanying drawings. It should be noted that the terms "upper," "lower," and the like are used herein for purposes of illustration only and not limitation.

Herein, ordinal words such as "first" and "second" cited in the present application are merely identifiers and do not have any other meaning, such as a particular order or the like.

In the following description, a detailed structure will be presented for a thorough understanding of embodiments of the present application. It will be apparent that embodiments of the application may be practiced without limitation to the specific details that are set forth by those skilled in the art. Preferred embodiments of the present application are described in detail below, however, the present application may have other embodiments in addition to these detailed descriptions.

The application provides an experimental device. The experimental set-up can be used to test two thrust bearings simultaneously. The two thrust bearings include a first thrust bearing 101 and a second thrust bearing 103. The thrust bearing has a housing and a thrust output shaft 102 penetrating the housing.

Referring to fig. 1-5, the experimental device includes a drive assembly 110, a gear box 200, a universal coupling 201, a first transition flange 202, and a second transition flange 203. The drive assembly 110 may be a drive motor. The drive output shaft 111 of the drive assembly 110 is connected to the gear input shaft of the gearbox 200. The gear output shaft of the gear box 200 is connected to one end of the universal joint 201. The other end of the universal coupling 201 is connected to one end of a first transition flange 202. The other end of the first transition flange 202 is connected to one end of the thrust output shaft 102 of the first thrust bearing 101. The other end of the thrust output shaft 102 of the first thrust bearing 101 is connected to one end of a second transition flange 203. The other end of the second transition flange 203 is connected to one end of the thrust output shaft 102 of the second thrust bearing 103. In this way, the drive motor may apply torque to the thrust output shaft 102 of the thrust bearing.

As shown in fig. 1 and 2, the experimental set-up further comprises a thrust bracket 120 and a thrust assembly 130. The thrust bracket 120 is fixedly disposed on the ground.

In the axial direction of the drive output shaft 111, the thrust assembly 130 is located between the first thrust bearing 101 and the second thrust bearing 103. The thrust assembly 130 includes first and second portions spaced apart along the axial direction of the drive output shaft 111. The first portion is for abutment to the housing of the first thrust bearing 101. The second portion is for abutting against the housing of the second thrust bearing 103 to apply forces in directions parallel to the axial direction of the drive output shaft 111 to the housing of the first thrust bearing 101 and the housing of the second thrust bearing 103, respectively.

Specifically, the thrust assembly 130 is movably coupled to the thrust bracket 120 in an axial direction of the drive output shaft 111. The thrust assembly 130 is retractable in the axial direction of the drive output shaft 111. In this way, the dimension of the thrust assembly 130 in the axial direction of the drive output shaft 111 can be increased (elongated) so that one end of the thrust assembly 130 abuts against the housing of the first thrust bearing 101 and the other end abuts against the housing of the second thrust bearing 103, thereby applying a force to the housing of the first thrust bearing 101 and the housing of the second thrust bearing 103. The direction of the force is parallel to the axial direction of the drive output shaft 111. By reducing (shortening) the size of the thrust assembly 130 in the axial direction of the drive output shaft 111, the thrust assembly 130 can be separated from the first thrust bearing 101 and the second thrust bearing 103, and the force of the thrust assembly 130 on the first thrust bearing 101 and the second thrust bearing 103 can be released.

It will be appreciated that in embodiments not shown, the thrust assembly may include a rack, a first gear, a first portion, a second gear, and a second portion. The first gear is connected to the first portion. The second gear is connected to the second portion. The first gear and the second gear are both rotatably engaged to the rack. The rack is fixedly connected to the thrust bracket. The length direction of the rack is parallel to the axial direction of the drive output shaft. Thus, the first gear rotates to drive the first portion to move along the axial direction of the driving output shaft so as to abut against the housing of the first thrust bearing and apply a force to the housing of the first thrust bearing. The second gear rotates to drive the second part to move along the axial direction of the driving output shaft so as to be abutted to the shell of the second thrust bearing and apply acting force to the shell of the second thrust bearing.

In this embodiment, torque can be applied to the first thrust bearing 101 and the second thrust bearing 103 by the driving motor, and a force with an axial direction parallel to the axial direction of the driving output shaft 111 can be applied to the first thrust bearing 101 and the second thrust bearing 103 by the thrust assembly 130, so that the thrust bearings can be tested more effectively; in addition, the first thrust bearing 101 and the second thrust bearing 103 can be tested at the same time, and the test efficiency is high.

Preferably, as shown in FIG. 2, thrust assembly 130 includes a first thrust assembly 137 and a second thrust assembly 138. Along the width direction (up-down direction of fig. 2) of the thrust bracket 120, the first thrust assembly 137 is located on one side of the axis of the drive output shaft 111, and the second thrust assembly 138 is located on the other side of the axis of the drive output shaft 111. The distance between the first thrust assembly 137 and the axis of the drive output shaft 111 and the distance between the second thrust assembly 138 and the axis of the drive output shaft 111 are equal in the width direction of the thrust bracket 120. Wherein, the width direction of the thrust bracket 120 is perpendicular to the axial direction of the drive output shaft 111, and the width direction of the thrust bracket 120 is perpendicular to the height direction of the thrust bracket 120. Thus, the two thrust assemblies 130 simultaneously apply the above-described forces to the first thrust bearing 101 and the second thrust bearing 103, and the first thrust bearing 101 and the second thrust bearing 103 can be tested more effectively.

The thrust bracket 120 is located between the first thrust bearing 101 and the second thrust bearing 103 in the axial direction of the drive output shaft 111. Thus, the thrust bracket 120 has a simple structure.

Thrust bracket 120 has an upwardly opening arcuate mounting slot 121. The experimental set-up also included a fixture configured as an arc-shaped structure. The fixing member is attached to the thrust bracket 120 at the arc-shaped mounting groove 121 to form a mounting hole with the arc-shaped mounting groove 121. The axial direction of the mounting hole is parallel to the axial direction of the drive output shaft 111. The thrust assembly 130 is disposed within the arcuate mounting slot 121. The thrust assembly 130 is disposed through the mounting hole. In this way, the thrust assembly 130 is able to move within the mounting bore in the axial direction of the mounting bore. Thereby facilitating installation of the thrust assembly 130. The positioning of the fasteners prevents the thrust assembly 130 from exiting the thrust bracket 120.

Preferably, the housing of the thrust bearing includes an upper housing 104 and a lower housing 105. The lower end of the upper housing 104 is connected to the upper end of the lower housing 105. Along the height of thrust bracket 120, thrust assembly 130 is located at the junction of upper housing 104 and lower housing 105. In this way, the thrust assembly 130 can abut the upper housing 104 and the lower housing 105. Thereby, the first thrust bearing 101 and the second thrust bearing 103 can be tested more effectively.

Referring to fig. 1 to 3, the thrust assembly 130 includes a thrust member 131 and an elongated shaft 132 (an example of a first portion). The thrust member 131 is retractable in the axial direction of the drive output shaft 111. The thrust member 131 may be a thrust hydraulic cylinder. The thrust hydraulic cylinder includes a cylinder body and a piston rod (an example of a second portion) provided with a piston. The cylinder body is provided with a first liquid port and a second liquid port. The piston is located in the cylinder body to divide the cylinder body into a first space and a second space. The first liquid port is communicated with the first space. The second liquid port is communicated with the second space. One end of the cylinder body is provided with an opening for the piston rod to extend out. Correspondingly, the thrust cylinder of the first thrust assembly 137 is a first thrust cylinder. The thrust cylinders of the second thrust assembly 138 are second thrust cylinders. Therefore, the magnitude of the acting force can be conveniently controlled.

As shown in fig. 3, one end of the thrust member 131 is connected to one end of the extension shaft 132. Specifically, the extension shaft 132 is connected to an end of the cylinder that is remote from the opening. Thereby, the dimension of the thrust assembly 130 in the axial direction of the drive output shaft 111 can be increased. The maximum dimension between the first thrust bearing 101 and the second thrust bearing 103 in the axial direction of the drive output shaft 111 may be increased.

Further preferably, as shown in FIG. 3, the thrust assembly 130 further includes a connection sleeve 135 and a fastener. The fastener may be a screw. One end of the connecting sleeve 135 has a sleeve opening and the other end is closed.

The length-increasing shaft 132 includes a major segment 133 and a minor segment 134. The diameter of the large section 133 is greater than the diameter of the small section 134. The large segment 133 and the small segment 134 are coaxially arranged. The large section 133 is connected to the small section 134. The large section 133 is located at the end of the elongated shaft 132. Thus, both ends of the extension shaft 132 are constructed in a stepped structure.

The large section 133 is arranged in the connecting sleeve 135. The fastener penetrates the peripheral wall of the connecting sleeve 135 and extends between the outer peripheral surface of the large segment 133 and the outer peripheral surface of the small segment 134. In this way, the fastener can block the large section 133 from exiting the connection sleeve 135. Thereby, the connection between the extension shaft 132 and the connection sleeve 135 is facilitated.

The experimental set-up also includes a pressure sensor 136. The connection sleeve 135 includes a first connection sleeve and a second connection sleeve. The one end of the first connecting sleeve, which is far away from the sleeve opening, is attached to the one end of the cylinder body, which is far away from the opening, and is connected to the cylinder body through a fastener. Thus, one end of the extension shaft 132 is connected to the cylinder body through the first coupling sleeve. The other end of the extension shaft 132 is connected to a second connection sleeve. The pressure sensor 136 may be attached to an end of the second connection sleeve remote from the opening and connected to the second connection sleeve by a fastener. The pressure sensor 136 is used to collect the amount of force applied by the thrust assembly 130 as described above. Thus, the magnitude of the acting force can be collected in real time.

The experimental setup includes a radial loading assembly 140. The radial loading assembly 140 includes a radial loading shaft 141. One end of the radial loading shaft 141 is connected to the thrust output shaft 102. The radial loading assembly 140 is capable of applying a downward directed radial force to the radial loading shaft 141. Thereby, a radial force can be applied to the thrust output shaft 102 to more effectively test the thrust bearing.

Specifically, as shown in fig. 4, the radial loading assembly 140 further includes a pull rod 142, a pull rod bracket 143, a hydraulic cylinder 144, a radial base 145, a pull plate 146, a bearing 148, a compression ring 149, and a nut. The radial base 145 is fixedly disposed on the ground. The hydraulic ram 144 is fixedly connected to the radial base 145. The middle of the pulling plate 146 is connected to the piston rod of the hydraulic ram 144. Thus, the hydraulic ram 144 can drive the pulling plate 146 up and down.

The tie rod bracket 143 is located above the radial base 145 and is fixedly coupled to the radial base 145. The upper end of the pull rod bracket 143 is provided with an oil groove 147. The oil groove 147 opens upward. The shape of the oil groove 147 corresponds to the shape of the bearing 148. The lower end of the bearing 148 is provided with an oil groove 147. Lubricating oil is provided in the oil groove 147 for lubricating the bearing 148.

The radial loading shaft 141 is provided to penetrate the inner ring of the bearing 148 so as to be rotatable with respect to the outer ring of the bearing 148. The compression ring 149 is constructed in a semicircular arc-shaped structure. The intrados of the compression ring 149 near its center conforms to the upper end of the outer race of the bearing 148.

The number of the tie rods 142 is two. The two tie rods 142 include a first tie rod and a second tie rod. Along the width direction of the thrust bracket 120, a first tie rod is provided at one side of the radial loading shaft 141, and a second tie rod is provided at the other side of the radial loading shaft 141. The length direction of the tie rod 142 extends in the height direction of the thrust bracket 120. Both ends of the pull rod 142 are provided with external threads. One end of the pull rod 142 is threaded through the compression ring 149 and then connected to the nut. The other end of the pull rod 142 is threaded through the pull plate 146 and then coupled to a nut. In this way, the compression ring 149 may be compressed against the outer ring of the bearing 148 by rotating the nut.

Referring to fig. 4, hydraulic ram 144 applies a downward hydraulic force to pulling plate 146. The hydraulic force can apply a downward radial force to the outer ring of the bearing 148 by the tie rod 142, and thus the thrust output shaft 102 connected to the radial loading shaft 141 receives the downward radial force. At this time, the bearing 148 is provided so that the radial direction loading shaft 141 can rotate while receiving a radial force. Thus, the radial loading assembly 140 is simple in structure.

It is further preferable that the radial base 145 is provided with a guide groove extending in the height direction of the thrust bracket 120. The pulling plate 146 is inserted into the guide groove. In this way, the guide groove can guide the movement of the pulling plate 146 in the height direction of the thrust bracket 120.

Preferably, the gearbox 200 may be a reduction gearbox. Thereby, the torque output by the drive assembly 110 may be increased.

Returning to fig. 1 and 2, the experimental set-up further comprises a third transition flange 204. The radial loading assembly 140 includes a first radial loading assembly 150 and a second radial loading assembly 151. One end of the radial loading shaft 141 of the first radial loading assembly 150 is connected to an end of the universal coupling 201 remote from the drive assembly 110. The other end of the radial-loading shaft 141 of the first radial-loading assembly 150 is connected to the end of the first transition flange 202 remote from the first thrust bearing 101.

One end of the radial loading shaft 141 of the second radial loading assembly 151 is connected to one end of the third transition flange 204. The other end of the third transition flange 204 is connected to the end of the second thrust bearing 103 remote from the first thrust bearing 101. Thus, both ends of the two thrust bearing assemblies are provided with radial loading assemblies 140. Thereby, the first thrust bearing 101 and the second thrust bearing 103 can be more accurately tested.

The radial loading assembly 140 also includes a first oil feed pump (not shown) and a second oil feed pump (not shown). The first feed pump is separated from the second feed pump. The first oil feed pump is connected to the hydraulic ram 144 of the first radial-loading assembly 150 via an oil line to feed oil to the hydraulic ram 144 of the first radial-loading assembly 150.

The second oil feed pump is connected to the hydraulic cylinder 144 of the second radial loading unit 151 through an oil pipe to feed oil to the hydraulic cylinder 144 of the second radial loading unit 151. The first oil feed pump and the second oil feed pump are both electrically connected to a controller that follows. Thus, the controller may control the operation of the first and second oil feed pumps, respectively, and thus the radial force exerted by the first radial loading assembly 150, and the radial force exerted by the second radial loading assembly 151, respectively.

Returning to fig. 1 and 2, the experimental apparatus further comprises a mounting base. The mounting blocks include a first mounting block 160 and a second mounting block 162. The first mount 160 and the second mount 162 are disposed at intervals along the axial direction of the drive output shaft 111, and the thrust bracket 120 is located between the first mount 160 and the second mount 162. The first thrust bearing 101 and the first radial loading assembly 150 are both connected to a first mount 160. In this way, the force of the first radial load assembly 150 on the first thrust bearing 101 is ultimately received by the first mount 160. The second thrust bearing 103 and the second radial load assembly 151 are both connected to a second mount 162. In this way, the force of the second radial load assembly 151 on the second thrust bearing 103 is ultimately received by the second mount 162.

As shown in fig. 5, the second mount 162 is provided with a connection long hole 164. The long axis of the connection long hole 164 is parallel to the axial direction of the drive output shaft 111. The second thrust bearing 103 is connected to the second mount 162 by a connection long hole 164 and a fastener (bolt and nut).

During operation of the experimental device, the second thrust bearing 103 moves relative to the second mount 162 in the axial direction of the drive output shaft 111. Of the forces of the thrust assembly 130 received by the second thrust bearing 103, one portion is received by the second thrust bearing 103 and the other portion is offset by friction generated by sliding of the second thrust bearing 103.

To this end, the experimental set-up also includes a roller 163. The roller 163 has a cylindrical structure. The second mount 162 is provided with a roller mounting hole. The roller 163 is rotatably connected to the second mount 162 about its own axis and is located within the roller mounting aperture. The axis of the roller 163 is parallel to the width direction of the thrust bracket 120. The upper edge of the roller 163 is slightly higher than the upper surface of the second mount 162.

The housing of the second thrust bearing 103 is connected to the upper surface of the second mount 162 and overlaps the roller 163. Thereby, the friction force between the second thrust bearing 103 and the second mount 162 can be reduced.

Preferably, the first mount 160 is connected to the connection location of the upper housing 104 and the lower housing 105 of the first thrust bearing 101. The second mount 162 is connected to the lower end of the lower housing 105 of the second thrust bearing 103.

The second mount 162 may be provided with a weight-reducing hole 161 to reduce the weight of the second mount 162.

The experimental set-up also included an adjustment shim (not shown). The adjustment shims may be used to mount the drive assembly 110, the gearbox 200, the radial loading assembly 140, the first thrust bearing 101, the second thrust bearing 103, and the thrust bracket 120 as needed to adjust the heights of the drive assembly 110, the gearbox 200, the radial loading assembly 140, the first thrust bearing 101, the second thrust bearing 103, and the thrust assembly 130.

The experimental set-up also included a hydraulic system. As shown in fig. 6, the hydraulic assembly further includes a double pilot operated check valve 178, a first shut-off valve 179, and a second shut-off valve 180. The first shut-off valve 179 and the second shut-off valve 180 may each be a manual shut-off valve for controlling flow.

The double pilot operated check valve 178 has a first pilot operated outlet 189, a second pilot operated outlet 190, a first pilot operated inlet 191, and a second pilot operated inlet 192. The first pilot operated outlet 189 is connected to the inlet of the first shut-off valve 179 through an oil line. The outlet of the first shut-off valve 179 is connected to the first port of the first thrust cylinder via an oil line. The outlet of the first shut-off valve 179 is also connected to the first port of the second thrust cylinder by another oil line.

The second pilot operated outlet 190 communicates through tubing to the inlet of the second shut-off valve 180. The outlet of the second shut-off valve 180 is connected to the second port of the first thrust cylinder by an oil line. The outlet of the second shut-off valve 180 is also connected to a second fluid port of a second thrust cylinder through another oil line.

Referring to fig. 6, in the case of inputting oil to the first pilot-operated inlet 191, in the double pilot-operated check valve 178, the first pilot-operated inlet 191 is in communication with the first pilot-operated outlet 189, and the second pilot-operated outlet 190 is in communication with the second pilot-operated inlet 192. In this way, oil enters the first space of the first thrust cylinder via the first pilot outlet 189 and the first shut-off valve 179, acting on the piston rod of the first thrust cylinder. In this way, the first thrust cylinder is extended to apply the aforementioned force to the first thrust bearing 101 and the second thrust bearing 103. In this process, the oil in the second space of the first thrust cylinder can be discharged. In this manner, oil in the second space of the first thrust cylinder is discharged through the second shut-off valve 180 and the second pilot operated outlet 190 to the second pilot operated inlet 192.

With continued reference to fig. 6, in the case of inputting oil to the first pilot-operated inlet 191, the oil passing through the first stop valve 179 also enters the first space of the second thrust cylinder, thereby acting on the piston rod of the second thrust cylinder. In this way, the second thrust cylinder is extended to apply the aforementioned force to the first thrust bearing 101 and the second thrust bearing 103. In this process, the oil in the second space of the second thrust hydraulic cylinder can be discharged. In this manner, oil within the second space of the second thrust cylinder is discharged through the second shut-off valve 180 and the second pilot operated outlet 190 to the second pilot operated inlet 192.

Referring to fig. 6, in the case of inputting oil to the second pilot-operated inlet 192, in the double pilot-operated check valve 178, the first pilot-operated inlet 191 and the first pilot-operated outlet 189 are connected, and the second pilot-operated outlet 190 and the second pilot-operated inlet 192 are connected. In this way, the oil enters the second space of the first thrust cylinder via the second pilot operated outlet 190 and the second shut-off valve 180, thereby acting on the piston rod of the first thrust cylinder. In this way, the first thrust cylinder shortens to contact the aforementioned forces on the first thrust bearing 101 and the second thrust bearing 103. In this process, the oil in the first space of the first thrust hydraulic cylinder may be discharged. In this manner, oil in the first space of the first thrust cylinder is discharged to the first pilot inlet 191 via the first shutoff valve 179 and the first pilot outlet 189.

Referring to fig. 6, in the case of inputting oil to the second pilot operated inlet 192, the oil passing through the second pilot operated outlet 190 and the second stop valve 180 also enters the second space of the second thrust cylinder to act on the piston rod of the second thrust cylinder. In this way, the second thrust cylinder shortens to release the aforementioned forces on the first thrust bearing 101 and the second thrust bearing 103. In this process, the oil in the first space of the second thrust cylinder can be discharged. In this manner, the oil in the first space of the second thrust cylinder is discharged to the first pilot operated inlet 191 via the first shutoff valve 179 and the first pilot operated outlet 189.

With continued reference to fig. 6, the hydraulic assembly further includes a tank 170, a reversing valve 177, and a pump. The reversing valve 177 may be a three-position four-way reversing valve. The reversing valve 177 has a first reversing port 185, a second reversing port 186, a third reversing port 187, and a fourth reversing port 188. The spool of the direction valve 177 is movable between a first communication position and a second communication position. When the direction valve 177 is in the first communication position, the first direction opening 185 and the fourth direction opening 188 communicate with each other, and the second direction opening 186 and the third direction opening 187 communicate with each other. When the direction valve 177 is located at the second communication position, the first direction changing port 185 and the third direction changing port 187 are communicated, and the second direction changing port 186 and the fourth direction changing port 188 are communicated.

The third reversing port 187 is connected to the first pilot operated inlet 191 by an oil line. The fourth reversing port 188 is coupled to a second pilot operated inlet 192 via tubing. The second reversing port 186 communicates through an oil line to the oil tank 170. The pump outlet of the pump communicates through an oil line to a first reversing port 185 of a reversing valve 177. The pump inlet of the pump communicates through an oil line to the oil tank 170. Therefore, the hydraulic assembly is simple in structure and convenient to control.

Specifically, the pumps include a first pump 172 and a second pump 173. The hydraulic assembly also includes a one-way valve 184. The pump outlet of the first pump 172 is connected to the first reversing inlet via an oil line. The pump outlet of the second pump 173 communicates through an oil line to the inlet of the one-way valve 184. The outlet of the check valve 184 communicates to an oil line that communicates with the pump outlet of the first pump 172.

Further preferably, as shown in fig. 6, the hydraulic assembly further comprises a pressure regulating valve. The pressure regulating valve is provided with a pressure regulating inlet and a pressure regulating outlet.

The pressure regulating valves include a first pressure regulating valve 174, a second pressure regulating valve 175, and a third pressure regulating valve 176.

The pressure regulating inlet of the first pressure regulating valve 174 is connected to an oil pipe that communicates with the pump outlet of the first pump 172 through an oil pipe. The pressure regulating outlet of the first pressure regulating valve 174 is connected to the second reversing port 186 through an oil pipe.

The pressure regulating inlet of the second pressure regulating valve 175 is connected to an oil pipe that communicates with the pump outlet of the first pump 172 through an oil pipe. The pressure regulating outlet of the second pressure regulating valve 175 is connected to the second reversing port 186 through an oil pipe.

The third pressure regulating valve 176 may be a pilot operated pressure regulating valve. The control port of the third pressure regulating valve 176 is connected to the pump outlet of the first pump 172 through an oil pipe. The pressure regulating inlet of the third pressure regulating valve 176 is connected to the inlet of the check valve 184 through an oil pipe. The pressure regulating outlet of the third pressure regulating valve 176 is connected to the second reversing port 186 through an oil pipe.

In the case of operation of the thrust assembly 130, the supply pressure may be adjusted by adjusting the first pressure regulating valve 174, the second pressure regulating valve 175, and the third pressure regulating valve 176.

Preferably, the hydraulic assembly further comprises a vent plug 171, a level gauge 183, a pressure gauge 181 and a pressure relay 182.

A level gauge 183 is provided to the tank 170 for detecting the level of the tank 170. A vent plug 171 is provided to the fuel tank 170 to allow the fuel tank 170 to communicate with the external environment.

The pressure gauge 181 is connected to the outlet of the first shut-off valve 179 through an oil pipe to collect the pressure of the outlet of the first shut-off valve 179 in real time. The pressure relay 182 communicates through an oil line to the outlet of the first shut-off valve 179 to collect a pressure signal representing the pressure of the outlet of the first shut-off valve 179 in real time.

The experimental set-up further comprises a controller. The controller is electrically connected to the driving assembly 110, the first pump 172, the second pump 173, the pressure regulating valve and the direction valve 177, thereby controlling the operations of the driving assembly 110, the first pump 172, the second pump 173, the pressure regulating valve and the direction valve 177 as needed. The controller is also electrically connected to the pressure sensor 136, the level gauge 183 and the pressure relay 182, thereby acquiring signals collected by the pressure sensor 136, the level gauge 183 and the pressure relay 182.

In the case where the thrust assembly 130 applies the above-described force to the first thrust bearing 101 and the second thrust bearing 103, when the pressure value indicated by the pressure signal collected by the pressure relay 182 is less than the preset pressure value, the controller controls the first pump 172 and the second pump 173 to operate, thereby supplying oil to the first space so that the pressure value indicated by the pressure signal increases to the preset pressure value.

In the case where the thrust assembly 130 applies the above-described force to the first thrust bearing 101 and the second thrust bearing 103, when the pressure indicated by the pressure signal collected by the pressure relay 182 reaches the preset pressure value, the first pump 172 and the second pump 173 stop operating so that the pressure indicated by the pressure signal collected by the pressure relay 182 is maintained at the preset pressure value.

When the signal collected by the level gauge 183 indicates that the level of the tank 170 is below a preset level, the controller sends a low level alarm signal.

Unless defined otherwise, technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application pertains. The terminology used herein is for the purpose of describing particular implementations only and is not intended to be limiting of the application. Terms such as "component" as used herein may refer to either a single part or a combination of parts. Terms such as "mounted," "disposed," and the like as used herein may refer to one component being directly attached to another component or to one component being attached to another component through an intermediary. Features described herein in one embodiment may be applied to another embodiment alone or in combination with other features unless the features are not applicable or otherwise indicated in the other embodiment.

The present application has been described in terms of the above embodiments, but it should be understood that the above embodiments are for purposes of illustration and description only and are not intended to limit the application to the embodiments described. Those skilled in the art will appreciate that many variations and modifications are possible in light of the teachings of the application, which variations and modifications are within the scope of the application as claimed.

Claims (11)

1. An experimental set-up for testing thrust bearings, the thrust bearings comprising a first thrust bearing and a second thrust bearing, the thrust bearings having a thrust output shaft, the experimental set-up comprising:

a drive assembly having a drive output shaft for connection to one end of the thrust output shaft of the first thrust bearing;

the thrust bracket is fixedly arranged;

the thrust assembly is located between the first thrust bearing and the second thrust bearing along the axial direction of the driving output shaft, the thrust assembly comprises a first part and a second part which are arranged at intervals along the axial direction of the driving output shaft, the first part is used for being abutted to the shell of the first thrust bearing, and the second part is used for being abutted to the shell of the second thrust bearing so as to apply acting forces with directions parallel to the axial direction of the driving output shaft to the shell of the first thrust bearing and the shell of the second thrust bearing respectively.

2. The experimental set-up according to claim 1, wherein the thrust assembly comprises a first thrust assembly and a second thrust assembly, the first thrust assembly being located on one side of the axis of the drive output shaft and the second thrust assembly being located on the other side of the axis of the drive output shaft, the distance between the first thrust assembly and the axis of the drive output shaft and the distance between the second thrust assembly and the axis of the drive output shaft being equal, the width direction of the thrust bracket being perpendicular to the axial direction of the drive output shaft and the height direction of the thrust bracket, in the width direction of the thrust bracket.

3. The experimental set-up according to claim 1, wherein the thrust bracket is located between the first thrust bearing and the second thrust bearing in an axial direction of the drive output shaft.

4. The experimental set-up according to claim 1, wherein the thrust assembly comprises a thrust member and an elongated shaft, the thrust member being retractable along an axial direction of the drive output shaft, one end of the thrust member being connected to one end of the elongated shaft.

5. The experimental device of claim 4, wherein the experimental device comprises a plurality of sample cells,

the thrust member includes a thrust cylinder, and/or

The thrust bracket is provided with an arc-shaped mounting groove with an upward opening, and the thrust component is arranged in the arc-shaped mounting groove.

6. The experimental set of claim 5, wherein the thrust assembly further comprises a connection sleeve and a fastener, the extension shaft comprises a large section and a small section having a diameter smaller than the diameter of the large section, the large section is positioned at an end of the extension shaft, one end of the connection sleeve is connected to the thrust member, the large section is disposed in the connection sleeve, and the fastener is disposed through a peripheral wall of the connection sleeve and extends between an outer peripheral surface of the large section and an outer peripheral surface of the small section.

7. The experimental set-up according to claim 1, further comprising a pressure sensor connected to one end of the thrust assembly in the axial direction of the drive output shaft for taking up the magnitude of the force.

8. The experimental set-up according to claim 1, comprising a radial loading assembly having one end of a radial loading shaft connected to the thrust output shaft, the radial loading assembly being capable of applying a downwardly directed radial force to the radial loading shaft.

9. The apparatus according to claim 8, wherein,

the radial loading assembly comprises a first radial loading assembly and a second radial loading assembly, one end of a radial loading shaft of the first radial loading assembly is connected to the drive output shaft, the other end of the radial loading shaft of the first radial loading assembly is connected to the thrust output shaft of the first thrust bearing,

an end of the radial loading shaft of the second radial loading assembly is connected to an end of the second thrust bearing remote from the first thrust bearing.

10. The experimental device of claim 1, wherein the device comprises a plurality of sensors,

the experimental device further comprises a mounting seat and a roller, wherein the mounting seat is provided with a connecting long hole with a long shaft parallel to the axial direction of the driving output shaft, the axial direction of the roller is parallel to the width direction of the thrust bracket, the roller is rotatably connected to the mounting seat, and the second thrust bearing is connected to the mounting seat through the connecting long hole and is lapped to the roller.

11. The apparatus according to claim 9, wherein the apparatus comprises,

the experimental device further comprises a first mounting seat and a second mounting seat, the first thrust bearing and the first radial loading assembly are connected to the first mounting seat, and the second thrust bearing and the second radial loading assembly are connected to the second mounting seat.