CN110398367B - Measuring device for measuring dynamic coefficient of sliding bearing - Google Patents
Measuring device for measuring dynamic coefficient of sliding bearing Download PDFInfo
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- CN110398367B CN110398367B CN201910593009.0A CN201910593009A CN110398367B CN 110398367 B CN110398367 B CN 110398367B CN 201910593009 A CN201910593009 A CN 201910593009A CN 110398367 B CN110398367 B CN 110398367B
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M13/00—Testing of machine parts
- G01M13/04—Bearings
Abstract
The invention provides a measuring device for measuring the dynamic coefficient of a sliding bearing, which is characterized by comprising the following components: a drive assembly; the rotating assembly is connected with the driving assembly and is driven to rotate by the driving assembly; the sliding bearing to be tested is arranged in the rotating component; the mounting shaft is mounted in the sliding bearing to be tested; a load assembly including a disc-shaped load disposed at an end of the mounting shaft; and the measuring assembly is positioned on the peripheral side of the disc-shaped load and is used for detecting the stress and the position movement of the disc-shaped load. And calculating the dynamic coefficient of the sliding bearing to be measured according to the data. The measuring device disclosed by the invention has the advantages that the driving assembly and the sliding bearing to be measured are connected through the rotating assembly, the mounting shaft is not in direct contact with other parts, the reliable measurement of the dynamic coefficient of the sliding bearing to be measured is realized, and the accurate measurement of the dynamic coefficient is ensured.
Description
Technical Field
The invention relates to the technical field of measuring equipment, in particular to a measuring device for measuring a dynamic coefficient of a sliding bearing.
Background
The sliding bearing has strong bearing capacity and high running precision, and is widely applied to rotating equipment such as steam turbines, precision machine tools and the like. The dynamic coefficients of the plain bearing include four stiffness coefficients and four damping coefficients. These dynamic coefficients can affect smooth operation of the rotor system. Accurate measurement of the dynamic coefficient of the sliding bearing plays an important role in the design and maintenance of the rotor system.
Scholars at home and abroad propose various measuring methods, including a pulse excitation identification method, an unbalanced response identification method, a multi-frequency excitation identification method, a sine excitation identification method and the like. The pulse excitation identification method can calculate the dynamic coefficient of the sliding bearing by applying excitation to the shaft and then recording the magnitude of the applied force and the axle center track. The experiment table for testing the dynamic rigidity of the sliding bearing is divided into an upright structure and an inverted structure. The test bed with the fixed experimental bearing is called a positive structure, and the test bed with the floating bearing is called an inverted mechanism.
The current sliding bearing dynamic coefficient measuring device is characterized in that a shaft is driven to rotate by a motor, and in the test process, for an inverted structure, a bearing in an experiment generally has an external support, and for an upright structure, a rotor is also connected with the motor, so that the accuracy of the dynamic coefficient is influenced.
Disclosure of Invention
Therefore, it is necessary to provide a measuring device for measuring the dynamic coefficient of the sliding bearing, which can ensure the accuracy of the dynamic coefficient, in order to solve the problem that the accuracy of the dynamic coefficient is poor due to the rotation of the shaft driven by the motor at present.
The above purpose is realized by the following technical scheme:
a measuring device for measuring the dynamic coefficient of a plain bearing, comprising:
a drive assembly;
the rotating assembly is connected with the driving assembly and is driven to rotate by the driving assembly; the sliding bearing to be tested is arranged in the rotating component;
the mounting shaft is mounted in the sliding bearing to be tested;
a load assembly including a disc-shaped load disposed at an end of the mounting shaft; and
and the measuring assembly is positioned on the peripheral side of the disc-shaped load and is used for detecting the stress and the position movement of the disc-shaped load.
In one embodiment, the number of the load assemblies is two, the number of the measuring assemblies is also two, the two load assemblies are respectively arranged at two ends of the mounting shaft, and the measuring assemblies are respectively arranged corresponding to the disc-shaped loads of the two load assemblies.
In one embodiment, the load assembly further comprises magnetic members which are oppositely arranged and generate repulsive force, wherein one of the magnetic members is arranged at the end of the mounting shaft, and the other magnetic member is mounted on the mounting frame.
In one embodiment, the load assembly further comprises an eccentric load disposed at an edge of the disc load away from the mounting shaft surface for balancing the friction torque of the mounting shaft.
In one embodiment, the rotating assembly includes a rotating housing, the sliding bearing to be tested is fixedly installed in the rotating housing, and the rotating housing is connected with the driving assembly.
In one embodiment, the measuring device further comprises two mounting bases, the two mounting bases are symmetrically arranged, the rotating assembly further comprises rolling bearings, and the rotating shell is mounted on the two mounting bases through the rolling bearings.
In one embodiment, the measuring assembly comprises an electromagnet and a pressure sensor positioned below the electromagnet, wherein the electromagnet is positioned on the peripheral side of the disc-shaped load and is spaced from the disc-shaped load;
and after the electromagnet is electrified, the electromagnet adsorbs the disc-shaped load, and the pressure sensor is used for recording the attraction force of the electromagnet on the disc-shaped load.
In one embodiment, the measuring assembly further comprises an eddy current sensor arranged on the periphery side of the disc-shaped load and having a preset distance with the electromagnet;
after the electromagnet adsorbs the disc-shaped load, the eddy current sensor is used for recording the position change of the axis of the disc-shaped load.
In one embodiment, the number of the electromagnets and the number of the pressure sensors are both multiple, and the electromagnets are arranged on the peripheral side of the disc-shaped load at intervals;
the number of the electric eddy current sensors is multiple, and the electric eddy current sensors are arranged at intervals.
In one embodiment, the measuring device further comprises an adjusting assembly, wherein the adjusting assembly is located between the magnetic pieces and the mounting frame and used for adjusting the distance between the two magnetic pieces.
In one embodiment, the adjusting assembly comprises an adjusting screw and a rotating arm, the adjusting screw is rotatably disposed on the mounting frame, the rotating arm is mounted at one end of the adjusting screw, and the magnetic member is mounted at the other end of the adjusting screw.
In one embodiment, the adjusting assembly further comprises a displacement sensor, and the displacement sensor is arranged on the mounting frame and used for recording the axial position of the mounting shaft.
After the technical scheme is adopted, the invention at least has the following technical effects:
according to the measuring device for measuring the dynamic coefficient of the sliding bearing, the driving assembly drives the rotating assembly to rotate so as to drive the sliding bearing to be measured to rotate, the mounting shaft cannot synchronously rotate along with the sliding bearing, at the moment, the measuring assembly can detect the attraction force borne by the disc-shaped load and the position change of the axis track of the disc-shaped load, and then the dynamic coefficient of the sliding bearing to be measured is calculated according to the data. The measuring device disclosed by the invention has the advantages that the driving assembly and the sliding bearing to be measured are connected through the rotating assembly, the mounting shaft is not in direct contact with other parts, the problem of poor dynamic coefficient accuracy caused by the rotation of the shaft driven by the motor at present is effectively solved, the reliable measurement of the dynamic coefficient of the sliding bearing to be measured is realized, and the accurate measurement of the dynamic coefficient is ensured.
Drawings
FIG. 1 is a perspective view of a measuring device according to an embodiment of the present invention from an angle;
FIG. 2 is a cross-sectional view of the measuring device shown in FIG. 1;
fig. 3 is a perspective view of the measuring device shown in fig. 1 from another angle.
Wherein:
100-a measuring device;
110-a drive assembly;
111-a drive motor;
112-a transmission member;
113-a motor base;
120-a rotating assembly;
121-rotating the housing;
122-rolling bearings;
130-mounting shaft;
140-a load assembly;
141-disc shaped load;
142-a magnetic member;
143-eccentric loading;
150-a measurement component;
151-an electromagnet;
152-a pressure sensor;
153-an eddy current sensor;
160-a mounting base;
170-a regulating component;
171-a mounting frame;
172-adjusting screw;
173-rotating arm;
174-displacement sensor;
200-sliding bearing to be tested.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the measuring device for measuring the dynamic coefficient of the sliding bearing according to the present invention is further described in detail by embodiments and with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.
The numbering of the components as such, e.g., "first", "second", etc., is used herein only to distinguish the objects as described, and does not have any sequential or technical meaning. The term "connected" and "coupled" when used in this application, unless otherwise indicated, includes both direct and indirect connections (couplings). In the description of the present invention, it is to be understood that the terms "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", and the like, indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be construed as limiting the present invention.
In the present invention, unless otherwise expressly stated or limited, the first feature "on" or "under" the second feature may be directly contacting the first and second features or indirectly contacting the first and second features through an intermediate. Also, a first feature "on," "over," and "above" a second feature may be directly or diagonally above the second feature, or may simply indicate that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature may be directly under or obliquely under the first feature, or may simply mean that the first feature is at a lesser elevation than the second feature.
Referring to fig. 1 to 3, the present invention provides a measuring device 100 for measuring the coefficient of dynamic of a plain bearing. The measuring device 100 is used for measuring the dynamic coefficient of the sliding bearing 200 to be measured. It should be noted that the measuring device 100 of the present invention can measure the force and position, and the dynamic coefficients of the sliding bearing, i.e. four stiffness coefficients and four damping coefficients, can be obtained by substituting the data into the calculation formula. It should be understood that the above calculation formula is an existing formula, and is not described herein in detail. The measuring device 100 is used for measuring the dynamic coefficient of the sliding bearing, realizing the reliable measurement of the dynamic coefficient of the sliding bearing 200 to be measured, ensuring the accuracy of the dynamic coefficient and realizing the accurate measurement.
In one embodiment, a measuring device 100 for measuring the coefficient of dynamic of a plain bearing includes a drive assembly 110, a rotating assembly 120, a mounting shaft 130, a load assembly 140, and a measuring assembly 150. The rotating assembly 120 is connected with the driving assembly 110 and is driven by the driving assembly 110 to rotate; the slide bearing 200 to be tested is mounted in the rotating assembly 120. The mounting shaft 130 is mounted in the slide bearing 200 to be tested. The load assembly 140 includes a disc-shaped load 141, the disc-shaped load 141 being disposed at an end of the mounting shaft 130. The measuring assembly 150 is located on the peripheral side of the disc-shaped load 141, and the measuring assembly 150 is used for detecting the force and the position play of the disc-shaped load 141.
The driving component 110 is a power source of the measuring apparatus 100, and is used for driving the rotating component 120 to drive the sliding bearing 200 to be measured to rotate, so that the measuring component 150 can measure corresponding data. Specifically, the driving assembly 110 includes a driving motor 111 and a transmission member 112 connecting the driving motor 111 and the rotating assembly 120. When the driving motor 111 works, the driving member 112 can be driven to move, and then the driving member 112 can drive the rotating assembly 120 and the sliding bearing 200 to be tested therein to rotate. Alternatively, the transmission 112 may be a belt transmission, which includes a pulley and a timing belt; a chain drive comprising a sprocket and a chain; but may also include gear drives and the like. Illustratively, the drive member 112 is a belt drive member. Alternatively, the driving motor 111 is mounted on a reference surface such as the ground through a motor base 113.
The rotating assembly 120 is used for installing the sliding bearing 200 to be tested, and driving the sliding bearing 200 to be tested to rotate, and the sliding bearing 200 to be tested is sleeved on the installation shaft 130. The sliding bearing 200 to be tested is installed in the rotating element 120, and the relationship between the installation shaft 130 and the driving element 110 is established by the rotating element 120 and the sliding bearing 200 to be tested. Therefore, the mounting shaft 130 can be in oil film contact with the sliding bearing 200 to be measured in the rotating process, and can avoid direct contact between the sliding bearing 200 to be measured and the driving assembly 110, that is, the sliding bearing 200 to be measured is not in direct contact with other parts, so that the accuracy of the dynamic coefficient can be ensured, and the accuracy of the measured dynamic coefficient can be ensured.
The load assembly 140 is disposed on the mounting shaft 130 for limiting the rotation of the mounting shaft 130 along with the sliding bearing 200 to be tested. Specifically, in the process that the rotating component 120 drives the sliding bearing 200 to be tested to rotate, a friction torque is given to the mounting shaft 130 due to the oil film action in the sliding bearing 200 to be tested, so that the mounting shaft 130 rotates along with the sliding bearing 200 to be tested. However, the mounting shaft 130 may be restricted from rotating with the sliding bearing 200 to be tested after the load assembly 140 is disposed on the mounting shaft 130. In this way, the measuring component 150 may shift the position of the load component 140 to measure the shift of the load component 140, and the measuring component 150 obtains the corresponding parameter. Specifically, a disc-shaped load 141 is provided at the end of the mounting shaft 130 and cooperates with the measuring device 100.
Alternatively, the disc-shaped load 141 has a hollow mounting portion that can be sleeved on the end of the mounting shaft 130; of course, the disc-shaped load 141 may have a flat plate-like structure and be directly fixed to the end of the mounting shaft 130. Illustratively, a disc-shaped load 141 is sleeved on the end of the mounting shaft 130. The axial center of the disc-shaped load 141 coincides with the axial center of the mounting shaft 130, and the measuring assembly 150 acts on the disc-shaped load 141 to shift the disc-shaped load 141. When the position of the disc-shaped load 141 moves, the mounting shaft 130 also moves, and the axis of the mounting shaft 130 changes to some extent. In this way, the measurement assembly 150 can detect the position change of the axial center of the mounting shaft 130 and the stress condition of the disc shaped load 141. And then, substituting the measured parameters into a calculation formula to obtain the dynamic parameters of the sliding bearing 200 to be measured.
By adopting the measuring device 100 of the above embodiment to measure the dynamic coefficient of the sliding bearing 200 to be measured, the mounting shaft 130 is not in direct contact with other parts, and the driving component 110 and the sliding component are connected through the rotating component 120, so that the problem of poor accuracy of the dynamic coefficient caused by the rotation of the shaft driven by the motor at present is effectively solved, the reliable measurement of the dynamic coefficient of the sliding bearing 200 to be measured is realized, and the accurate measurement of the dynamic coefficient is ensured.
In one embodiment, the number of the load assemblies 140 is two, the number of the measuring assemblies 150 is also two, the two load assemblies 140 are respectively arranged at two ends of the mounting shaft 130, and the measuring assemblies 150 are respectively arranged corresponding to the disc-shaped loads 141 of the two load assemblies 140. It is understood that the number of the load assemblies 140 is two, and two load assemblies 140 are respectively disposed at both ends of the mounting shaft 130. Therefore, the stress balance of the installation shaft 130 can be ensured, the eccentric falling problem is avoided, and the installation shaft 130 can be installed on the sliding bearing 200 to be tested in a balance manner, so that the dynamic coefficient of the sliding bearing 200 to be tested is accurately measured. Correspondingly, the number of the measuring assemblies 150 is also two, and the two measuring assemblies are respectively arranged corresponding to the two load assemblies 140, so that the accuracy of the measured data and the accuracy of the dynamic coefficient measurement can be ensured.
In one embodiment, the measuring device 100 further comprises two mounting bases 160, and the two mounting bases 160 are symmetrically arranged. The two mounting bases 160 are used for mounting the measuring assembly 150 and the rotating assembly 120 respectively, so as to ensure that the position of the measuring assembly 150 is fixed. The rotating assembly 120 is located between the two mounting bases 160 and rotatably mounted to the two mounting bases 160, and the two measuring assemblies 150 are respectively disposed on the surfaces of the mounting bases 160 and corresponding to the disc-shaped loads 141 of the load assembly 140. The mounting base 160 is mounted on a reference surface such as the ground. Illustratively, the mounting base 160 includes a base and a side plate vertically disposed on the base, the measuring assembly 150 is disposed on the base and the side plate, and two ends of the rotating assembly 120 are rotatably mounted in the two side plates.
In one embodiment, the rotating assembly 120 includes a rotating housing 121, the sliding bearing 200 to be tested is fixedly mounted in the rotating housing 121, and the rotating housing 121 is connected to the driving assembly 110. The outer side of the rotating housing 121 is connected to the transmission member 112, for example, the synchronous belt of the transmission member 112 is sleeved on the outer side of the rotating housing 121, and the sliding bearing 200 to be tested is fixedly mounted in the rotating housing 121. Alternatively, the sliding bearing 200 to be tested may be fixedly provided by a screw or the like. Illustratively, the rotating housing 121 is a hollow ring-shaped structure. Optionally, the part of the rotating housing 121 that is engaged with the transmission member 112 has a toothed portion for increasing the friction between the rotating housing 121 and the transmission member 112, so as to avoid a slip phenomenon, and ensure that the rotating housing 121 can rotate synchronously with the driving motor 111.
In one embodiment, the rotating assembly 120 further comprises rolling bearings 122, and the rotating housing 121 is mounted to the two mounting bases 160 through the rolling bearings 122. The two rolling bearings 122 are sleeved on the rotating housing 121, the inner ring of the rolling bearing 122 is fixedly connected with the rotating housing 121, and the outer ring of the rolling bearing 122 is fixedly connected with the mounting base 160. Thus, the rotating housing 121 can be ensured to reliably rotate relative to the mounting base 160, avoiding interference with the mounting base 160 and ensuring smooth rotation.
In one embodiment, the load assembly 140 further includes magnetic members 142 disposed opposite to each other and generating a repulsive force, wherein one of the magnetic members 142 is disposed at an end of the mounting shaft 130, and the other magnetic member 142 is mounted to the mounting frame 171. The magnetic member 142 is used for installing the installation shaft 130 in the sliding bearing 200 to be tested in a suspension manner, so as to further ensure that the installation shaft 130 is not contacted with any part and ensure the accuracy of dynamic coefficient measurement; meanwhile, because the magnetic members 142 are disposed at the two ends of the mounting shaft 130, the mounting shaft 130 can be mounted on the sliding bearing 200 to be tested at a proper position, so that the mounting shaft 130 is prevented from moving axially.
Specifically, each end of the mounting shaft 130 has two magnetic members 142, one of the magnetic members 142 is disposed at the end of the mounting shaft 130 and outside the disc-shaped load 141, and the other magnetic member 142 is disposed at the mounting bracket 171. The two magnetic members 142 may directly correspond and generate a repulsive force. That is, the polarities of the opposing surfaces of the two magnetic members 142 are the same. Since the magnetic members 142 at the two ends of the mounting shaft 130 are both disposed in a repulsive manner, the mounting shaft 130 can be disposed in the sliding bearing 200 to be tested in a floating manner. Moreover, the magnetic members 142 at the two ends of the mounting shaft 130 are stressed the same, and the position of the mounting shaft 130 in the bearing to be tested can be automatically adjusted, so that the mounting shaft 130 is symmetrically arranged and stressed in a balanced manner, the generation of deflection is avoided, the axial movement of the mounting shaft 130 can be prevented, and the position fixation of the mounting shaft 130 in the sliding bearing 200 to be tested is ensured. Alternatively, the magnetic member 142 may be disposed in a ring shape or a sheet shape. Alternatively, the magnetic member 142 may be a permanent magnet. It is understood that the mounting brackets 171 may be fixedly connected with the rotating housing 121, and may also be fixedly connected with the fixed portion, and of course, one of the mounting brackets 171 may also be fixedly connected with the rotating housing 121, and the other mounting bracket 171 may also be fixedly connected with the fixed portion.
In one embodiment, the load assembly 140 further includes an eccentric load 143, the eccentric load 143 being disposed at an edge of the disc load 141 away from the surface of the mounting shaft 130 for balancing the friction torque of the mounting shaft 130. When the eccentric load 143 is eccentrically disposed on the disc load 141, a certain eccentric moment is generated due to a certain distance between the eccentric load 143 and the axial center of the disc load 141. Thus, when the rotating component 120 drives the sliding bearing 200 to be tested to rotate, the oil film in the sliding bearing 200 to be tested can provide a friction torque to the mounting shaft 130, so that the mounting shaft 130 rotates along with the sliding bearing 200 to be tested. After the mounting shaft 130 rotates to a certain angle, the eccentric loads 143 on both sides of the mounting shaft 130 generate eccentric torque to balance the friction torque, so that the mounting shaft 130 does not rotate along with the sliding bearing 200 to be tested. At this time, the mounting shaft 130 is in a relatively stationary state, and the measuring assembly 150 can measure the attractive force to the disc load 141 and the axial play of the mounting shaft 130. Alternatively, the eccentric load 143 includes, but is not limited to, an eccentric protrusion, etc., and may be other structures eccentrically disposed at the edge of the disc shaped load 141.
In one embodiment, the measurement assembly 150 includes an electromagnet 151 and a pressure sensor 152 located below the electromagnet 151, the electromagnet 151 being located on a peripheral side of the disc-shaped load 141 and spaced apart from the disc-shaped load 141. When the electromagnet 151 is energized, the electromagnet 151 attracts the disc-shaped load 141, and the pressure sensor 152 records the attraction force of the electromagnet 151 to the disc-shaped load 141. The electromagnet 151 is used to generate a suction force to the disc-shaped load 141, so that the disc-shaped load 141 moves the mounting shaft 130. Thus, the pressure sensor 152 can measure the attraction force of the electromagnet 151 on the mounting shaft 130. After the electromagnet 151 and the pressure sensor 152 are combined, attraction force can be applied to the disc-shaped load 141, and the accurate value of the attraction force can be obtained through the pressure sensor 152, so that the accuracy of measuring the dynamic coefficient of the sliding bearing 200 to be measured is ensured.
In one embodiment, the measuring assembly 150 further includes an eddy current sensor 153, and the eddy current sensor 153 is disposed on the circumferential side of the disc-shaped load 141 and has a predetermined distance from the electromagnet 151. After the electromagnet 151 attracts the disc-shaped load 141, the eddy current sensor 153 records a change in the position of the axial center of the disc-shaped load 141. When the eddy current sensor 153 is energized, the change in the axial position of the disc-shaped load 141 can be recorded in real time, and the change in the axial position of the mounting shaft 130 can be obtained. Thus, the dynamic coefficient of the sliding bearing 200 to be measured can be calculated conveniently. Alternatively, eddy current sensor 153 is mounted to mounting base 160 via a mounting base.
In one embodiment, the number of the electromagnets 151 and the pressure sensors 152 is plural, and the plural electromagnets 151 are arranged at intervals on the circumferential side of the disc-shaped load 141. The number of the eddy current sensors 153 is plural, and the plural eddy current sensors 153 are provided at intervals. The electromagnets 151 are arranged at intervals, and the eddy current sensors 153 are arranged at intervals, so that the electromagnets 151 and the eddy current sensors 153 are also arranged at intervals, and influence between each other can be avoided.
Illustratively, in each measuring assembly 150, the number of the electromagnets 151 and the pressure sensors 152 is two. I.e. two electromagnets 151 at the end of each mounting shaft 130. The two electromagnets 151 are respectively disposed in the horizontal direction and the vertical direction of the end portion of the mounting shaft 130, as shown in fig. 1, one of the electromagnets 151 is disposed on the bottom plate of the mounting base 160, and the other electromagnet 151 is disposed on a mounting plate vertically disposed at the rear side of the mounting base 160. A pressure sensor 152 is provided below each electromagnet 151. The two eddy current sensors 153 are disposed in the horizontal direction and the vertical direction of the end of the mounting shaft 130, and are different from the position where the electromagnet 151 is disposed, as shown in fig. 1, the two eddy current sensors 153 are respectively disposed opposite to the electromagnet 151 and are disposed on the side plate of the mounting base 160. Alternatively, two eddy current sensors 153 may be disposed at both ends of the mounting shaft 130, or two eddy current sensors 153 may be disposed at one end of the mounting shaft 130.
In an embodiment, the measuring apparatus 100 further includes an adjusting assembly 170, and the adjusting assembly 170 is located between the magnetic members 142 and the mounting frame 171 and is used for adjusting the distance between the two magnetic members 142. The adjustment assembly 170 is used to adjust the axial position of the mounting shaft 130. Specifically, the adjustment assembly 170 may be moved in a direction toward the mounting shaft 130 and may also be moved in a direction away from the mounting shaft 130. Thus, the magnetic force between the magnetic members 142 corresponding to the adjustment assembly 170 is changed, such as increased or decreased, and the mounting shaft 130 can be moved in the axial direction by the repulsive force of the magnetic members 142 to readjust the axial position of the mounting shaft 130.
Alternatively, the number of the adjustment assemblies 170 may be one, and in this case, after the distance between the two magnetic members 142 is adjusted by one adjustment assembly 170, the magnetic force at one end of the mounting shaft 130 may be changed, and accordingly, the mounting shaft 130 may be moved in the axial direction to re-level to maintain the balance state. Moreover, the two magnetic members 142 on one side of the mounting shaft 130 are located between the mounting shaft 130 and the adjusting assembly 170, and the two magnetic members 142 on the other side of the mounting shaft 130 are located between the mounting shaft 130 and the supporting frame, as shown in fig. 3, one of the magnetic members 142 is fixed to the rotating housing 121 through the supporting frame. Of course, in other embodiments of the present invention, the number of the adjusting assemblies 170 may be two, and the two adjusting assemblies are respectively disposed corresponding to the two ends of the mounting shaft 130.
In one embodiment, the adjusting assembly 170 includes an adjusting screw 172 and a rotating arm 173, the adjusting screw 172 is rotatably disposed on the mounting bracket 171, the rotating arm 173 is mounted at one end of the adjusting screw 172, and the magnetic member 142 is mounted at the other end of the adjusting screw 172. When the rotating arm 173 rotates, the adjusting screw 172 can be driven to move along the axial direction, so that the two magnetic members 142 are close to or away from each other, so as to adjust the magnitude of the repulsive force between the magnetic members 142, and further adjust the axial position of the mounting shaft 130.
In one embodiment, the adjustment assembly 170 further includes a displacement sensor 174, the displacement sensor 174 being disposed on the mounting bracket 171 for registering the axial position of the mounting shaft 130. Alternatively, the displacement sensor 174 includes, but is not limited to, a laser sensor or the like. The displacement sensor 174 may detect the spacing between it and the disc load 141 to determine the axial position of the mounting shaft 130. As can be appreciated, as the adjustment assembly 170 moves toward the mounting shaft 130, the distance between the displacement sensor 174 and the disc load 141 decreases; as the adjustment assembly 170 moves in a direction closer to the mounting shaft 130, the distance between the displacement sensor 174 and the disc shaped load 141 increases. In this way the axial position of the mounting shaft 130 is recorded in real time.
When the measuring device 100 of the present invention is used, the motor 111 is first driven to rotate the rotating case 121 via the timing belt. Since the sliding bearing 200 to be tested is connected to the rotating casing 121 by the fastener, the sliding bearing 200 to be tested can rotate together with the rotating casing 121. Due to the action of the oil film in the sliding bearing 200 to be tested, a friction torque is given to the mounting shaft 130. After the mounting shaft 130 is rotated to a certain angle, the friction torque of the sliding bearing 200 to be tested is balanced by the eccentric load 143, so that the middle mounting shaft 130 does not rotate along with the rotating housing 121. Because the mounting bracket 171 is connected to the adjusting screw 172 by using a screw thread, when the rotating arm 173 rotates, the adjusting screw 172 can be driven to rotate, and the axial position of the mounting shaft 130 can be adjusted by the repulsive force between the two magnetic members 142. At the same time, the displacement sensor 174 on the mounting bracket 171 can record the axial position of the mounting shaft 130 in real time.
By applying a current to the electromagnets 151, the electromagnets 151 are caused to generate an attractive force to the disc-shaped load 141, and at the same time, the magnitude of the attractive force generated by the electromagnets 151 to the mounting shaft 130 is recorded by the pressure sensor 152 corresponding to each electromagnet 151. The eddy current sensor 153 can record the axial position change of the disc-shaped load 141, and further obtain the axial position change of the mounting shaft 130. The dynamic coefficient of the sliding bearing 200 to be measured can be calculated by substituting the data into a calculation formula.
The technical features of the embodiments described above can be arbitrarily combined, and for the sake of brevity, all possible combinations of the technical features in the embodiments described above are not described, but should be considered as the scope of the present specification as long as there is no contradiction between the combinations of the technical features.
The above-mentioned embodiments only express several embodiments of the present invention, and the description thereof is more specific and detailed, but not construed as limiting the scope of the present invention. It should be noted that, for a person skilled in the art, several variations and modifications can be made without departing from the inventive concept, which falls within the scope of the present invention. Therefore, the protection scope of the present patent shall be subject to the appended claims.
Claims (10)
1. A measuring device for measuring the dynamic coefficient of a plain bearing, comprising:
a drive assembly;
the rotating assembly is connected with the driving assembly and is driven to rotate by the driving assembly; the sliding bearing to be tested is arranged in the rotating component;
the mounting shaft is mounted in the sliding bearing to be tested;
the load assembly comprises a disc-shaped load and magnetic members which are oppositely arranged and generate repulsive force, the disc-shaped load is arranged at the end part of the mounting shaft, one of the magnetic members is arranged at the end part of the mounting shaft, and the other magnetic member is arranged on the mounting frame; and
and the measuring assembly is positioned on the peripheral side of the disc-shaped load and is used for detecting the stress of the disc-shaped load and the axis locus of the disc-shaped load.
2. The measuring device of claim 1, wherein the number of the load assemblies is two, the number of the measuring assemblies is also two, the two load assemblies are respectively arranged at two ends of the mounting shaft, and the measuring assemblies are respectively arranged corresponding to the disc-shaped loads of the two load assemblies.
3. A measuring device as claimed in claim 2, wherein the load assembly further comprises an eccentric load provided at an edge of the disc-shaped load remote from the mounting shaft surface for balancing the friction torque of the mounting shaft.
4. A measuring device according to any one of claims 1 to 3, wherein the rotating assembly comprises a rotating housing in which the sliding bearing to be measured is fixedly mounted, the rotating housing being connected to the drive assembly.
5. The measuring device of claim 4, further comprising two mounting bases, wherein the two mounting bases are symmetrically disposed, and wherein the rotating assembly further comprises a rolling bearing, and wherein the rotating housing is mounted to the two mounting bases through the rolling bearing.
6. A measuring device according to any one of claims 1 to 3, wherein the measuring assembly comprises an electromagnet and a pressure sensor located below the electromagnet, the electromagnet being located on a peripheral side of the disc-shaped load and spaced from the disc-shaped load;
after the electromagnet is electrified, the electromagnet adsorbs the disc-shaped load, and the pressure sensor is used for recording the attraction of the electromagnet to the disc-shaped load;
and further, the measuring assembly further comprises an eddy current sensor which is arranged on the peripheral side of the disc-shaped load and has a preset distance with the electromagnet;
after the electromagnet adsorbs the disc-shaped load, the eddy current sensor is used for recording the position change of the axis of the disc-shaped load.
7. The measuring device according to claim 6, wherein the number of the electromagnets and the number of the pressure sensors are plural, and the plural electromagnets are arranged at intervals on a peripheral side of the disc-shaped load;
the number of the electric eddy current sensors is multiple, and the electric eddy current sensors are arranged at intervals.
8. The measuring device of claim 1, further comprising an adjustment assembly between the magnetic members and the mounting bracket for adjusting a spacing between the two magnetic members.
9. The measuring device according to claim 8, wherein the adjusting assembly comprises an adjusting screw and a rotating arm, the adjusting screw is rotatably disposed on the mounting frame, the rotating arm is mounted at one end of the adjusting screw, and the magnetic member is mounted at the other end of the adjusting screw.
10. The measurement device of claim 9, wherein the adjustment assembly further comprises a displacement sensor disposed on the mounting bracket for recording an axial position of the mounting shaft.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910593009.0A CN110398367B (en) | 2019-07-03 | 2019-07-03 | Measuring device for measuring dynamic coefficient of sliding bearing |
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| CN102818701A (en) * | 2012-07-31 | 2012-12-12 | 浙江大学 | Similar test bed and test method for rotor-sliding bearing power |
| CN105865792A (en) * | 2016-05-26 | 2016-08-17 | 西北工业大学 | Textured sliding bearing experiment table with bearing rotating and journal fixed |
| CN106153342A (en) * | 2016-08-24 | 2016-11-23 | 上海交通大学 | Aero-engine heavy duty high speed bush(ing) bearing comprehensive performance testing device |
| CN108036947A (en) * | 2017-12-28 | 2018-05-15 | 上海建桥学院 | A kind of bearing test device for applying radially alternating load |
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| CN1793816A (en) * | 2005-12-30 | 2006-06-28 | 合肥工业大学 | Multifunction sliding bearing experimental platform |
| KR20110064997A (en) * | 2009-12-09 | 2011-06-15 | 한국생산기술연구원 | Simulator for sliding bearing of construction machines |
| CN101995310A (en) * | 2010-11-15 | 2011-03-30 | 河南科技大学 | Test device of frictional characteristic of sliding bearing under middle and heavy radial load |
| CN102410915A (en) * | 2011-07-27 | 2012-04-11 | 周其斗 | Electromagnetic excitation shaft loading device |
| CN102818701A (en) * | 2012-07-31 | 2012-12-12 | 浙江大学 | Similar test bed and test method for rotor-sliding bearing power |
| CN105865792A (en) * | 2016-05-26 | 2016-08-17 | 西北工业大学 | Textured sliding bearing experiment table with bearing rotating and journal fixed |
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