CN113295311A - Method for determining friction torque between rolling bearing roller and raceway and testing device - Google Patents

Method for determining friction torque between rolling bearing roller and raceway and testing device Download PDF

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CN113295311A
CN113295311A CN202110460855.2A CN202110460855A CN113295311A CN 113295311 A CN113295311 A CN 113295311A CN 202110460855 A CN202110460855 A CN 202110460855A CN 113295311 A CN113295311 A CN 113295311A
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rolling bearing
bearing
load
friction torque
rotating shaft
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CN113295311B (en
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孙守光
王曦
李强
侯宇
邹骅
刘志明
王文静
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Beijing Jiaotong University
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Beijing Jiaotong University
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    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
    • G01L5/00—Apparatus for, or methods of, measuring force, work, mechanical power, or torque, specially adapted for specific purposes
    • G01L5/0009—Force sensors associated with a bearing
    • 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

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Abstract

The invention provides a method for determining the friction torque between a roller and a raceway of a rolling bearing and a testing device, wherein under the condition that the rotating speed of the rolling bearing is known, the functional relation between the total friction torque M of the rolling bearing and an external load P is M (P), and the variation of the total friction torque M mainly comprises the friction torque M between the roller and the raceway related to the external loadFThe applied load P is divided into n sections, and the friction moment M between the roller and the roller path is caused when the applied load is PFCan be driven by load from PiChange to Pi+1Increment of friction moment delta M between time roller racewaysFAnd (4) accumulating to obtain. A device for testing the friction torque of the horizontal rolling bearing is also provided to realize the determination method. The invention creates important conditions for the state evaluation and fatigue life prediction of the rolling bearing.

Description

Method for determining friction torque between rolling bearing roller and raceway and testing device
Technical Field
The invention belongs to the technical field of bearing testing, and relates to a method and a device for determining friction torque between a rolling bearing roller and a raceway.
Background
The total friction torque of the rolling bearing includes friction torque between the roller and the raceway, friction torque between the roller and the retainer, drag friction torque between each component in the bearing and lubricating oil (grease), and the like. The existing experimental device and method are suitable for testing the total friction torque of the rolling bearing, namely the sum of all the friction torques. At present, an effective method for testing the friction torque between the roller and the raceway of the rolling bearing is lacked, and the friction torque between the roller and the raceway is a key mechanical parameter for evaluating the rolling contact fatigue reliability of the raceway of the bearing and predicting the service life of the raceway of the bearing.
The friction force between the roller and the raceway makes the bearing raceway easier to peel off, and the fatigue life of the bearing is obviously shortened. Therefore, the friction torque between the rolling bearing roller and the raceway is accurately detected, and important conditions are created for obtaining the friction force between the roller and the raceway, so that the bearing state evaluation and the fatigue life prediction are realized.
Disclosure of Invention
Aiming at the defects of the prior art, the invention provides a method for determining the friction torque between a roller and a raceway of a rolling bearing and a testing device for realizing the determination method, and provides a technical means for further realizing comprehensive stress evaluation and state prediction of the rolling bearing.
In order to realize the purpose, the following technical scheme is adopted:
a method for determining the friction torque between the roller and the raceway of a rolling bearing is disclosed, wherein the function relation between the total friction torque M and the applied load P of the rolling bearing is M (P) under the condition that the rotating speed of the rolling bearing is known, and the total friction of the rolling bearingThe friction moment M is the friction moment M between the roller and the roller pathFAnd the rest of the friction torque MLThe sum of (a) and (b), i.e.:
M(P)＝MF(P)+ML(P) (1)
wherein the friction torque M between the roller and the racewayFWhen the external load is zero, the value is zero, and the external load is generated only when the rolling bearing has the external load, and the magnitude of the external load is strongly related to the external load; and other frictional torque MLWhether or not the rolling bearing is subjected to an applied load, it is always present as long as the bearing rotates, its magnitude being weakly or not correlated with the applied load, and its variation with load, if any, being a high order small quantity compared to the friction torque between the roller and the raceway.
For a certain applied load P*In a smaller load range delta P nearby, the variation of the total friction moment M is mainly determined by the friction moment M between the roller and the raceway related to the applied load PFCause, when the applied load P is P*At Δ P/2, the total friction moment M is:
Figure BDA0003042172840000021
when the applied load P is P*At + Δ P/2, the total friction moment M is:
Figure BDA0003042172840000031
thus, for a certain applied load P*In a nearby smaller load range Δ P, the variation Δ M of the total friction moment M is:
ΔM(P*)＝ΔMF(P*)＝kF(P*)ΔP (4)
wherein k isF(P) shows a frictional moment M between the roller and the racewayFSlope at applied load P, i.e. from a certain applied load P*The friction force between the roller and the raceway can be obtained by the variation delta M of the total friction moment M of the rolling bearing in a certain small load range delta P nearbyMoment MFChange curve of the applied load P at a certain applied load P*Slope k of (d)F(P*)；
The method is characterized in that: the determination method is to obtain the friction moment M between the roller and the raceway of the rolling bearing by testing the total friction moment of the rolling bearing in different loading states with high precision under the condition of keeping the rotating speed unchangedFSlope k of curve with applied load P at applied load PF(P), and further obtaining the friction torque M between the roller and the raceway of the rolling bearing by a piecewise linear summation methodFCurve with applied load P.
The method for determining the friction torque between the roller and the raceway of the rolling bearing is characterized in that:
the determination method comprises the steps of dividing an external load P into n sections, wherein n is a natural number greater than 2, and each load node is marked as Pi(i ═ 0,1,2, …, n), where P0For dead-weight loads of rolling bearings and their shafts without additional mass, PnLoad from PiChange to Pi+1Load change amount at time is Δ Pi+1Can be driven by a load from PiChange to Pi+1Increment of friction moment delta M between time roller racewaysFThe friction torque M between the roller and the raceway is obtained by accumulation and calculationFNamely:
Figure BDA0003042172840000041
a testing device for realizing the method for determining the friction torque between the roller and the raceway of the rolling bearing is characterized in that: the device comprises a rotating shaft, a loading bearing, a rolling bearing A, a rolling bearing B, a loading bearing seat, a driving device, a first annular mass disc and a second annular mass disc, wherein the first annular mass disc and the second annular mass disc are arranged on the rotating shaft and can adjust weight;
the testing device is in a horizontal layout, the axis of the rotating shaft is parallel to the horizontal plane, one end of the rotating shaft is in power connection with the driving device and is in matched connection with the inner rings of the rolling bearing A, the loading bearing and the rolling bearing B in sequence, the rolling bearing A is fixed with the outer ring of the rolling bearing B, the outer ring of the loading bearing is in matched connection with the loading bearing seat, and an external load P is applied to the loading bearing through the loading bearing seat;
the first annular mass disc and the loading bearing are located on two opposite sides of the rolling bearing A, and the second annular mass disc and the loading bearing are located on two opposite sides of the rolling bearing B.
The test device, wherein: the loading bearing seat comprises an upper supporting plate structure, and an external load P is applied to the loading bearing through the upper supporting plate structure.
The test device, wherein: the rotating shaft is provided with shaft shoulders used for installing the rolling bearing A, the rolling bearing B and the inner ring of the loading bearing respectively.
The test device, wherein: and an output shaft of the driving device is connected with or separated from one end of the rotating shaft through a clutch device.
The test device, wherein: the rotating shaft device further comprises a rotating speed sensor capable of detecting the rotating angular speed of the rotating shaft.
The test device, wherein: the system also comprises a data processing system for receiving the data of the rotating speed sensor and calculating and processing the data.
The test device further comprises the following using method:
passing mass of PIFirst annular mass plate and mass PIIThe second annular mass disc loads the loading bearing, the self weight of the rotating shaft is considered, and the external radial load of the rotating shaft on the loading bearing is PcThe two ends of the rotating shaft bear the weight P respectivelyIAnd PIIThe rotating shaft is respectively subjected to radial support reaction forces R borne by the two rolling bearings at the rolling bearing A and the rolling bearing BAAnd RBThe action can be obtained according to the equilibrium equation:
Figure BDA0003042172840000051
the distance between the loading bearing and the rolling bearing A and the distance between the loading bearing and the rolling bearing B are both L, the distance between the first annular quality disc and the rolling bearing A is L, and the distance between the second annular quality disc and the rolling bearing B is also L;
the weight of the first annular mass disc and the weight of the second annular mass disc are adjusted for three times, and the rolling bearing A and the rolling bearing B are measured for three times; the combination linearity of radial support reaction force variation borne by the rolling bearing A and the rolling bearing B in the measuring process is irrelevant by adjusting the weights of the first annular mass disc and the second annular mass disc under the condition of not changing the rotational inertia of a rotary shaft system;
according to the friction torque difference information generated by two sets of linear independent radial support reaction force changes borne by the two rolling bearings in the measuring process, the friction torque M between the two rolling bearing rollers and the raceway is analyzedFThe slope of the curve changing with the applied load P at the bearing reaction force is obtained, so that the friction moment M between the rolling bearing roller and the raceway is obtained by a piecewise linear accumulation method according to the formula (5)FCurve with applied load P.
The test device, wherein:
first measuring friction moment M1: applying an external load to the loading bearing, and recording the sum of the applied load and the gravity load of the rotating shaft and the components thereof as PcIn this step, no annular quality discs, i.e. P, are mounted at either end of the shaftI＝PIIAs 0, according to equation (6), the radial support reaction forces applied to the rolling bearing a and the rolling bearing b are:
Figure BDA0003042172840000061
measuring friction moment M for the second time2: keeping the load applied by the loading bearing unchanged, adding the first annular mass disc and the second annular mass disc at two ends of the rotating shaft, wherein the weight P of the first annular mass discI(2L + L) Δ P/L, weight of the second annular mass plateQuantity PIIΔ P; according to the formula (6), the radial bearing reaction forces borne by the rolling bearing A and the rolling bearing B are respectively obtained as follows:
Figure BDA0003042172840000071
third measurement of Friction Torque M3: keeping the load applied by the loading bearing unchanged, and adjusting the weight of the first annular mass disc and the second annular mass disc at the two ends of the rotating shaft and the weight P of the first annular mass discIΔ P, weight P of the second annular mass plateII(2L + L) Δ P/L; according to the formula (6), the radial bearing reaction forces borne by the rolling bearing A and the rolling bearing B are respectively obtained as follows:
Figure BDA0003042172840000072
because the external load born by the loading bearing is unchanged under the condition of the three measurements, the variation of the friction torque obtained by the second measurement and the third measurement relative to the friction torque obtained by the first measurement is only formed by the sum of the variation of the friction torque of the rolling bearing A and the variation of the friction torque of the rolling bearing B, and a linear equation system is established for different angular velocities within the range of the measured angular velocity:
Figure BDA0003042172840000073
according to the formulae (7) to (9), the compounds are obtained
Figure BDA0003042172840000074
Through a formula (11), friction torque M between the rolling bearing A and the rolling bearing B and the roller path is obtained through decoupling respectivelyFRadial bearing reaction force P borne by change curve of applied load PcSlope k at/2AAnd kB。
The test device, wherein: adjusting the applied load P applied to the loading bearing, repeating the above process to respectively obtain the friction torque M between the roller path and the rolling track of the rolling bearing A and the rolling bearing BFSlope k of curve with applied load P under the condition of increasing radial support reaction forceAAnd kB。
Compared with the prior art, the invention has the following advantages and beneficial effects:
1. the invention provides a method for determining the friction torque between a roller and a raceway of a rolling bearing through a piecewise linear approximation idea, which can calculate and obtain the friction torque between the roller and the raceway and provide a theoretical basis for further analyzing fatigue and service life evaluation of the rolling bearing.
2. The experimental device disclosed by the invention adopts the two rolling bearings as the supporting parts of the rotating shaft, and meanwhile, in the free rotation process of the rotating shaft, no other factors interfere the rotation process of the rotating shaft, so that the problem that the friction torque of the supporting bearing caused by the use of the supporting bearing when the rolling bearing is loaded and the friction torque testing precision of the rolling bearing are influenced by other factors is solved.
3. According to the invention, by adjusting the mass and distribution of the annular mass discs on the two ends of the rotating shaft, the combination linearity of the radial support reaction variation borne by the rolling bearing A and the rolling bearing B in the measuring process is irrelevant under the condition of not changing the rotary inertia of a rotary shaft system; the friction torque M between the two rolling bearing rollers and the raceway is analyzed according to the friction torque difference information generated by the two rolling bearing two groups of linear independent radial support reaction force changes in the measuring processFThe slope of the curve changing along with the external load P at the bearing reaction force realizes the decoupling solution of the linear equation set of two-dimensional, and realizes the high-precision decoupling measurement.
4. The invention realizes the loading of the tested rolling bearing A and the tested rolling bearing B through the loading bearing, and can realize the application of larger radial load.
Drawings
FIG. 1 is a schematic diagram of the relationship between the total friction moment M and the applied load P of the rolling bearing and the piecewise linear calculation (rotation speed omega);
FIG. 2 shows the determination of the friction torque M between the rollers and the raceways of a rolling bearing using the piecewise linear conceptFSchematic diagram (rotational speed ω);
FIG. 3 is a schematic diagram of a friction torque experimental device for a horizontal rolling bearing according to the present invention;
FIG. 4 is a force analysis diagram of the horizontal rolling bearing friction torque experimental device provided by the invention;
fig. 5A, 5B, and 5C are schematic diagrams of three previous and subsequent tests of the experimental device for friction torque between the roller and the raceway of the rolling bearing according to the present invention.
Description of reference numerals: a rotating shaft 1; a rolling bearing A21 and a rolling bearing B22; a rolling bearing A support seat 31; a rolling bearing B support base 32; a loading bearing 4; a load bearing housing 5; a first annular mass plate 61; a second annular mass disc 62; a base 7; a clutch device 8; a drive means 9.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is further described in detail below with reference to examples and accompanying drawings, and the exemplary embodiments and descriptions thereof are only used for explaining the present invention and are not meant to limit the present invention.
It should be noted that in the description of the present invention, the terms "lateral", "longitudinal", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
The following further describes the embodiments of the present invention with reference to the accompanying drawings.
The invention firstly provides a method for determining the friction torque between a rolling bearing roller and a raceway, which has the following principle:
the total friction moment M of the rolling bearing is related to the bearing load P and the rotational speed ω. At a given bearing speed ω, there is a functional relationship M (P) between the total bearing friction torque M and the applied load P, which is generally non-linear, as shown in fig. 1.
Meanwhile, the total friction moment M of the rolling bearing is the friction moment M between the roller and the racewayFAnd other frictional torque ML(including the friction torque between the roller and the cage, the drag friction torque between the components in the bearing and the lubricant, etc.) and the sum of:
M(P)＝MF(P)+ML(P) (1)
wherein the friction torque M between the roller and the racewayFWhen the external load is zero, the value is zero, and the external load is generated only when the rolling bearing has the external load, and the magnitude of the external load is strongly related to the external load; and other frictional torque MLWhether or not the rolling bearing is subjected to an applied load, it is always present as long as the bearing rotates, its magnitude being weakly or not correlated with the applied load, and its variation with load, if any, being a high order small quantity compared to the friction torque between the roller and the raceway.
Thus, for the load P*In a small load range delta P nearby, the variation of the total friction moment M of the bearing is mainly determined by the friction moment M between the roller and the raceway which is strongly related to the applied loadFContribution, i.e. when the applied load P is P*Δ P/2, the total bearing friction moment is (as shown in FIG. 1):
Figure BDA0003042172840000111
when the applied load is P*The total friction moment of the bearing at + delta P/2 is as follows:
Figure BDA0003042172840000112
thus, for the load P*In a certain smaller load range delta P nearby, the variation delta M of the total friction moment M of the bearing is
ΔM(P*)＝ΔMF(P*)＝kF(P*)ΔP (4)
Wherein k isF(P) shows a frictional moment M between the roller and the racewayFSlope at applied load P, i.e. from a certain applied load P*The variation delta M of the total friction moment M of the rolling bearing in a certain small load range delta P nearby can obtain the friction moment M between the roller and the racewayFChange curve of the applied load P at a certain applied load P*Slope k of (d)F(P*)。
Therefore, the friction torque M between the rolling bearing roller and the raceway under a certain rotating speed omega and with the external load P can be obtained through piecewise linear accumulationF. FIG. 2 shows the determination of the friction moment M between the rollers and the raceways of the bearing proposed by the present inventionF(P*) The piecewise linear idea of (1). As shown in fig. 2, the applied load P is divided into n segments, and each load node is denoted as Pi(i ═ 0,1,2, …, n), where P0For dead-weight loads of rolling bearings and their shafts without additional mass, PnLoad from PiChange to Pi+1Load change amount at time is Δ Pi+1. Friction moment M between roller paths when external load is PFCan be driven by load from PiChange to Pi+1Increment of friction moment delta M between time roller racewaysFAnd (3) accumulating to obtain:
Figure BDA0003042172840000121
the method for determining the friction torque of the rolling bearing roller and the raceway provided by the invention needs to carry out high-precision test on the total friction torque of the same rolling bearing in different loaded states, so that the friction torque M between the rolling bearing roller and the raceway is obtained according to the formula (4)FSlope k of the curve with load P at load PF(P) further rootAccording to the formula (5), the friction torque M between the rolling bearing roller and the raceway is obtained by a piecewise linear accumulation methodFCurve with load P.
The invention also provides an experimental device capable of testing the friction torque of the horizontal rolling bearing under different loading states. Fig. 3 shows a horizontal rolling bearing friction torque experimental device of the present invention, which includes a rotating shaft 1, a rolling bearing a 21, a rolling bearing b 22, a rolling bearing a supporting seat 31, a rolling bearing b supporting seat 32, a loading bearing 4, a loading bearing seat 5, a first annular mass plate 61, a second annular mass plate 62, a base 7, a clutch device 8, a driving device 9, a control loading device (not shown), a rotation speed sensor (not shown), and a data processing system (not shown).
The first rolling bearing supporting seat 31 and the second rolling bearing supporting seat 32 are fixedly connected with the base 7; the first rolling bearing supporting seat 31 and the second rolling bearing supporting seat 32 are respectively provided with inner cylindrical surfaces matched with outer cylindrical surfaces of outer rings of the first rolling bearing 21 and the second rolling bearing 22; the inner cylindrical surfaces of the first rolling bearing support seat 31 and the second rolling bearing support seat 32 are coaxial; the rotating shaft 1 is respectively provided with shaft shoulders for installing inner rings of a rolling bearing A21, a rolling bearing B22 and a loading bearing 4; the rotating shaft 1 can be provided with a first annular mass disc 61 and a second annular mass disc 62 with different masses at two ends.
The rotating components on the rotating shaft system comprise the rotating shaft 1, the rolling bearing A21, the rolling bearing B22, the loading bearing 4, the first annular quality disc 61 and the second annular quality disc 62, and the rotating components on the rotating shaft system comprise the rotating shaft 1, the rolling bearing A21, the rolling bearing B22, an inner ring of the loading bearing 4, a rolling body and a retainer, the first annular quality disc 61 and the second annular quality disc 62; the rotating shaft system is in a horizontal layout, and the axis of the rotating shaft 1 is parallel to the horizontal plane. An output shaft of the driving device is connected with or separated from one end of the rotating shaft 1 through a clutch device 8; the rotating speed sensor is used for detecting the rotating angular speed of the rotating shaft; the data processing system is used for receiving and processing the rotation angular speed signal of the rotating shaft 1 detected by the rotating speed sensor.
The stress analysis of the horizontal rolling bearing friction torque experimental device is shown in fig. 4, the stress analysis is carried out by taking the rotating shaft 1 as an object, the loading bearing 4 is loaded by controlling the loading device in the test process, the dead weight of the rotating shaft 1 is considered, and the external radial load of the rotating shaft 1 on the loading bearing 4 is PcThe two ends of the rotating shaft bear the weight P respectivelyIAnd PIIThe rotating shaft 1 is subjected to radial support reaction forces R borne by two rolling bearings at the rolling bearing A21 and the rolling bearing B22 respectivelyAAnd RBThe action can be obtained according to the equilibrium equation:
Figure BDA0003042172840000141
when a friction torque test is carried out by using the horizontal rolling bearing friction torque experimental device, under the condition of applying a certain load to the loading bearing 4, three times of measurement are carried out on the rolling bearing A21 and the rolling bearing B22; by adjusting the mass and the distribution of the first annular mass disc 61 and the second annular mass disc 62 at the two ends of the rotating shaft 1, the combination linearity of the radial support reaction variation borne by the rolling bearing A21 and the rolling bearing B22 in the measuring process is irrelevant under the condition of not changing the rotary inertia of a rotating shaft system; the friction torque M between the bearing rollers and the raceways of the rolling bearings A21 and B22 is analyzed according to the friction torque difference information generated by the two rolling bearings bearing two groups of linear independent radial support reaction force changes in the measurement processFThe slope of the curve varying with the load P at the bearing reaction force is obtained, so that the friction moment M between the rolling bearing roller and the raceway is obtained by a piecewise linear accumulation method according to the formula (5)FCurve with applied load P. Fig. 5A, 5B, and 5C show the implementation of these three measurements.
First measuring friction moment M1: applying an external load to the loading bearing 4, and recording the sum of the applied load and the gravity load of the rotating shaft 1 and the components thereof as PcThe step is notFirst annular mass discs 61, 62, i.e. P, are mounted at both ends of the shaft 1I＝PIIAs 0, according to equation (6), the radial support reaction forces received by the rolling bearing a 21 and the rolling bearing b 22 are:
Figure BDA0003042172840000142
measuring friction moment M for the second time2: keeping the load applied by the loading bearing 4 unchanged, adding a first annular mass plate 61 and a second annular mass plate 62 at two ends of the rotating shaft 1, setting the mass of one annular mass plate as delta P, and arranging (2L + L)/L first annular mass plates 61 at one end of the rotating shaft 1 close to the rolling bearing A21, namely PIA second annular mass disc 62, i.e. P, is arranged at the other end of the shaft 1, which is close to the roller bearing b 22, (2L + L) (. DELTA.P/L)IIΔ P; from the equation (6), it is understood that the radial support reaction forces received by the rolling bearing a 21 and the rolling bearing b 22 are:
Figure BDA0003042172840000151
third measurement of Friction Torque M3: keeping the load applied by the loading bearing 4 unchanged, adjusting a first annular quality disk 61 and a second annular quality disk 62 at two ends of the rotating shaft 1, setting the mass of one annular quality disk to be delta P, and arranging one first annular quality disk 61, namely P, at one end of the rotating shaft 1 close to the rolling bearing A21I(2L + L)/L second annular mass plate 62, i.e., P, is disposed at the other end of the rotating shaft close to the rolling bearing B22II(2L + L) Δ P/L; from the equation (6), it is understood that the radial support reaction forces received by the rolling bearing a 21 and the rolling bearing b 22 are:
Figure BDA0003042172840000152
because the external load borne by the loading bearing 4 is unchanged under the three measurement conditions, the variation of the friction torque obtained by the second measurement and the third measurement relative to the friction torque obtained by the first measurement is only formed by the sum of the variation of the friction torques of the rolling bearing A21 and the rolling bearing B22, and a linear system of two-dimensional equations is established for different angular velocities within the range of the measured angular velocities:
Figure BDA0003042172840000161
according to the formulae (7) to (9), the compounds are obtained
Figure BDA0003042172840000162
By the formula (11), the friction torque M between the rolling bearing A21 and the rolling bearing B22 rollers and the roller paths can be obtained by decoupling respectivelyFRadial bearing reaction force P borne by change curve of load PcSlope k at/2AAnd kB. Increasing the external load applied to the loading bearing 4, repeating the above processes, and obtaining the friction torque M between the roller and the raceway of the rolling bearing A21 and the rolling bearing B22 respectivelyFSlope k of curve with applied load P under the condition of increasing radial support reaction forceAAnd kB. Further, according to the formula (5), the friction torque M between the roller and the raceway of the rolling bearing A21 and the rolling bearing B22 is obtained by a piecewise linear accumulation methodFCurve with applied load P.
The measurement method provided by the invention comprises the following steps:
step one, mounting a loading bearing 4 at the middle shaft shoulder of a rotating shaft 1; installing an inner ring of a rolling bearing A21 at a shaft shoulder at one end of the rotating shaft 1, and installing an inner ring of a rolling bearing B22 at a shaft shoulder at the other end of the rotating shaft 1; and respectively matching the outer cylindrical surfaces of the outer rings of the rolling bearing A21 and the rolling bearing B22 with the inner cylindrical surfaces of the two test bearing seats 31 and 32. On the premise of ensuring the installation requirement, the rotating shaft 1 and the components thereof have certain rotational inertia, and the gravity load of the rotating shaft 1 and the components thereof is recorded as P0。
Step two, loading the bearing4 applying an external load P, so that the applied load P and the gravity load P of the rotating shaft 1 and the components thereof0The sum is denoted PcIn this step, the first annular mass plate 61 and the second annular mass plate 62 are not installed at both ends of the rotating shaft 1.
And step three, the driving device 9 drives the rotating shaft 1 through the clutch device 8 to drive the inner rings of the rolling bearing A21 and the rolling bearing B22 to synchronously rotate, and angular speed signals of the rotating shaft 1 are collected. The rotating speed of the rotating shaft 1 is increased to a given value and kept stable, then the rotating shaft 1 is separated from the driving device 9 by the clutch device 8, the rotating shaft 1 rotates freely and decelerates under the combined action of the loading bearing 4, the friction torque of the rolling bearing A21 and the friction torque of the rolling bearing B22, and in the process, the angular speed signal of the rotating shaft 1 is continuously measured.
And step four, calculating the kinetic energy of all moving parts on the rotating shaft by adopting the rotating speed information obtained by the rotating shaft 1 angular speed data processing system to obtain the total kinetic energy-time relation of the rotating parts, and further calculating the change rate of the total kinetic energy, wherein the change rate of the kinetic energy is equal to the product of the bearing friction torque and the rotating shaft angular speed. Under the condition of obtaining the kinetic energy change rate and the angular speed of the rotating shaft, the total friction moment M of the loading bearing 4, the rolling bearing A21 and the rolling bearing B22 can be directly calculated1The variation with the rotation speed.
Step five, keeping the load applied by the loading bearing 4 unchanged, adding first annular quality disks 61 and 62 at two ends of the rotating shaft 1, setting the mass of one annular quality disk to be delta P, and arranging (2L + L)/L first annular quality disks 61 at one end of the rotating shaft 1 close to the rolling bearing shell 21, namely PIA second annular mass disc 62, i.e. P, is arranged at the other end of the shaft 1, which is close to the roller bearing b 22, (2L + L) (. DELTA.P/L)II＝ΔP。
Step six, repeating the step three and the step four to obtain the total friction moment M of the loading bearing 4, the rolling bearing A21 and the rolling bearing B222The variation with the rotation speed.
Step seven, keeping the load applied by the loading bearing 4 unchanged, adjusting the first annular quality disks 61 and 62 at the two ends of the rotating shaft 1, setting the mass of one annular quality disk as delta P, and arranging one first annular quality disk at one end of the rotating shaft 1 close to the rolling bearing A2161, i.e. PI(2L + L)/L second annular mass plate 62, i.e., P, is disposed at the other end of the rotating shaft close to the rolling bearing B22II＝(2L+l)ΔP/l。
Step eight, repeating the step three and the step four to obtain the total friction moment M of the loading bearing 4, the rolling bearing A21 and the rolling bearing B223The variation with the rotation speed.
Step nine, according to the composition of the sum of the friction torques of the loading bearing 4 and the two rolling shafts 21 and 22 under the three measurement conditions, the friction torques M between the rollers and the raceways of the rolling bearing A21 and the rolling bearing B22 are respectively obtained through the formula (11)FRadial bearing reaction force P borne by change curve of load PcSlope k at/2AAnd kB。
Step ten, continuously increasing the external load P applied to the loading bearing 4, repeating the step two to the step nine, and respectively obtaining the friction torque M between the roller and the raceway of the rolling bearing A21 and the rolling bearing B22FSlope k of curve with applied load P under the condition of increasing radial support reaction forceAAnd kB. Further, according to the formula (5), the friction torque M between the roller and the raceway of the rolling bearing A21 and the rolling bearing B22 is obtained by a piecewise linear accumulation methodFCurve with applied load P.
Therefore, the friction torque between the roller and the raceway of the rolling bearing A21 and the rolling bearing B22 under any rotating speed and any load working condition can be obtained by the method. To eliminate the possible influence of air resistance, the experimental apparatus should be placed in a vacuum environment if necessary.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.

Claims (10)

1. A method for determining the friction torque between the roller and the raceway of a rolling bearing, under the condition of known rotation speed of the rolling bearing, the functional relation between the total friction torque M and the applied load P of the rolling bearingM (P), the total friction moment M of the rolling bearing is the friction moment M between the roller and the racewayFAnd the rest of the friction torque MLThe sum of (a) and (b), i.e.:
M(P)＝MF(P)+ML(P) (1)
when the applied load P is P*At Δ P/2, the total friction moment M is:
Figure FDA0003042172830000011
when the applied load P is P*At + Δ P/2, the total friction moment M is:
Figure FDA0003042172830000012
therefore, for a small load range Δ P around a certain applied load P, the variation Δ M of the total friction torque M is:
ΔM(P*)＝ΔMF(P*)＝kF(P*)ΔP (4)
wherein k isF(P) shows a frictional moment M between the roller and the racewayFSlope at applied load P;
the method is characterized in that: the determination method is to obtain the friction moment M between the roller and the raceway of the rolling bearing by testing the total friction moment of the rolling bearing in different loading states with high precision under the condition of keeping the rotating speed unchangedFSlope k of curve with applied load P at applied load PF(P), and further obtaining the friction torque M between the roller and the raceway of the rolling bearing by a piecewise linear summation methodFCurve with applied load P.
2. A method of determining a friction torque between a roller and a raceway of a rolling bearing according to claim 1, characterized in that:
the determination method comprises the steps of dividing an external load P into n sections, wherein n is a natural number greater than 2, and each load nodeThe point is marked as Pi(i ═ 0,1,2, …, n), where P0For dead-weight loads of rolling bearings and their shafts without additional mass, PnLoad from PiChange to Pi+1Load change amount at time is Δ Pi+1Can be driven by a load from PiChange to Pi+1Increment of friction moment delta M between time roller racewaysFThe friction torque M between the roller and the raceway is obtained by accumulation and calculationFNamely:
Figure FDA0003042172830000021
3. a test device for carrying out the method for determining a friction torque between a roller and a raceway of a rolling bearing according to claim 1 or 2, characterized in that: the device comprises a rotating shaft, a loading bearing, a rolling bearing A, a rolling bearing B, a loading bearing seat, a driving device, a first annular mass disc and a second annular mass disc, wherein the first annular mass disc and the second annular mass disc are arranged on the rotating shaft and can adjust weight;
the testing device is in a horizontal layout, the axis of the rotating shaft is parallel to the horizontal plane, one end of the rotating shaft is in power connection with the driving device and is in matched connection with the inner rings of the rolling bearing A, the loading bearing and the rolling bearing B in sequence, the rolling bearing A is fixed with the outer ring of the rolling bearing B, the outer ring of the loading bearing is in matched connection with the loading bearing seat, and an external load P is applied to the loading bearing through the loading bearing seat;
the first annular mass disc and the loading bearing are located on two opposite sides of the rolling bearing A, and the second annular mass disc and the loading bearing are located on two opposite sides of the rolling bearing B.
4. The test device of claim 3, wherein: the loading bearing seat comprises an upper supporting plate structure, and an external load P is applied to the loading bearing through the upper supporting plate structure.
5. The test device of claim 3, wherein: the rotating shaft is provided with shaft shoulders used for installing the rolling bearing A, the rolling bearing B and the inner ring of the loading bearing respectively.
6. The test device of claim 3, wherein: and an output shaft of the driving device is connected with or separated from one end of the rotating shaft through a clutch device.
7. The test device of claim 3, wherein: the rotating shaft device also comprises a rotating speed sensor capable of detecting the rotating angular speed of the rotating shaft and a data processing system for receiving the data of the rotating speed sensor and calculating and processing the data.
8. The test device of claim 3, further comprising the following method of use:
passing mass of PIFirst annular mass plate and mass PIIThe second annular mass disc loads the loading bearing, the self weight of the rotating shaft is considered, and the external radial load of the rotating shaft on the loading bearing is PcThe two ends of the rotating shaft bear the weight P respectivelyIAnd PIIThe rotating shaft is respectively subjected to radial support reaction forces R borne by the two rolling bearings at the rolling bearing A and the rolling bearing BAAnd RBThe action can be obtained according to the equilibrium equation:
Figure FDA0003042172830000041
the distance between the loading bearing and the rolling bearing A and the distance between the loading bearing and the rolling bearing B are both L, the distance between the first annular quality disc and the rolling bearing A is L, and the distance between the second annular quality disc and the rolling bearing B is also L;
the weight of the first annular mass disc and the weight of the second annular mass disc are adjusted for three times, and the rolling bearing A and the rolling bearing B are measured for three times; the combination linearity of radial support reaction force variation borne by the rolling bearing A and the rolling bearing B in the measuring process is irrelevant by adjusting the weights of the first annular mass disc and the second annular mass disc under the condition of not changing the rotational inertia of a rotary shaft system;
according to the friction torque difference information generated by two sets of linear independent radial support reaction force changes borne by the two rolling bearings in the measuring process, the friction torque M between the two rolling bearing rollers and the raceway is analyzedFThe slope of the curve changing with the applied load P at the bearing reaction force is obtained by the method of piecewise linear accumulation to obtain the friction moment M between the rolling bearing roller and the racewayFCurve with applied load P.
9. The test device of claim 8, wherein:
first measuring friction moment M1: applying an external load to the loading bearing, and recording the sum of the applied load and the gravity load of the rotating shaft and the components thereof as PcIn this step, no annular quality discs, i.e. P, are mounted at either end of the shaftI＝PIIAs 0, according to equation (6), the radial support reaction forces applied to the rolling bearing a and the rolling bearing b are:
Figure FDA0003042172830000042
measuring friction moment M for the second time2: keeping the load applied by the loading bearing unchanged, adding the first annular mass disc and the second annular mass disc at two ends of the rotating shaft, wherein the weight P of the first annular mass discI(2L + L) Δ P/L, weight P of the second annular mass plateIIΔ P; according to the formula (6), the radial bearing reaction forces borne by the rolling bearing A and the rolling bearing B are respectively obtained as follows:
Figure FDA0003042172830000051
third measurement of Friction Torque M3: keeping the load applied by the loading bearing unchanged, and adjusting the weight of the first annular mass disc and the second annular mass disc at the two ends of the rotating shaft and the weight P of the first annular mass discIΔ P, weight P of the second annular mass plateII(2L + L) Δ P/L; according to the formula (6), the radial bearing reaction forces borne by the rolling bearings A and B are respectively obtained as follows:
Figure FDA0003042172830000052
because the external load born by the loading bearing is unchanged under the condition of the three measurements, the variation of the friction torque obtained by the second measurement and the third measurement relative to the friction torque obtained by the first measurement is only formed by the sum of the variation of the friction torque of the rolling bearing A and the variation of the friction torque of the rolling bearing B, and a linear equation system is established for different angular velocities within the range of the measured angular velocity:
Figure FDA0003042172830000053
according to the formulae (7) to (9), the compounds are obtained
Figure FDA0003042172830000061
Through a formula (11), friction torque M between the rolling bearing A and the rolling bearing B and the roller path is obtained through decoupling respectivelyFRadial bearing reaction force P borne by change curve of applied load PcSlope k at/2AAnd kB。
10. The test device of claim 9, wherein: adjusting the applied load P applied to the loading bearing, repeating the above process to respectively obtain the friction torque M between the roller path and the rolling track of the rolling bearing A and the rolling bearing BFLoad with outsideSlope k of the curve of variation of the load P in the event of an increase in the radial bearing force to which it is subjectedAAnd kB。
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