A method for equivalent calculation of friction coefficient between same type rolling bearings

Abstract

The present application relates to a kind of equivalent calculation method of friction coefficient between same type rolling bearing, method includes, establish equivalent transition parameter, remove interference factor etc. Draw large bearing comprehensive rotation friction force, large bearing comprehensive friction coefficient curve;Through curve fitting and extension etc. Smooth and extend the curve, obtain the comprehensive rotation friction coefficient of large bearing under the force condition of different values, comprehensive rotation friction force, to obtain the relevant parameters of large bearing under each working condition. The friction coefficient of same type small bearing can be obtained by equivalent analysis method. The technical principle of this method is to obtain the rotation friction coefficient of large bearing by using the measured data of rotation friction coefficient of same type small bearing, and to transfer the contact deformation area between rolling body and raceway. The technical problem of difficult measurement of original large bearing friction coefficient is effectively solved.

Description

Technical Field

[0001] This invention relates to a method for equivalent calculation of the friction coefficient between rolling bearings of the same type. It is mainly used when the friction coefficient of large bearings is difficult to measure, to measure the friction coefficient of small bearings of the same type, and to infer the friction coefficient of large bearings of the same type through equivalent analysis. Background Technology

[0002] Measuring various rotational friction parameters of large bearings requires the construction of large test benches and matching transport vehicles and lifting equipment such as heavy-duty gantry cranes. This requires a lot of manpower and resources, has a long measurement cycle, and yields scarce measurement data, making it difficult to prove the universality of the test measurement data.

[0003] Secondly, because the coefficient of rotational friction of a bearing changes under different stress conditions due to variations in the contact area, the test conditions need to cover all operating conditions of the bearing, resulting in an excessive amount of testing. Summary of the Invention

[0004] In view of the limitations of measuring the friction coefficient of large rolling bearings, the purpose of this invention is to provide an equivalent calculation method for the friction coefficient between rolling bearings of the same type. This method uses measured data of the rotational friction coefficient of small bearings of the same type and calculates the contact deformation area between the rolling elements and the raceway to transfer the friction coefficient of the large bearing.

[0005] The term "small bearing" in this scheme refers to bearings with a pitch circle diameter less than 3m; the term "large bearing" refers to bearings with a pitch circle diameter greater than that of the small bearing. That is, assuming the pitch circle diameter (inner diameter) of the small bearing is x, then x < 3m; and the pitch circle diameter (inner diameter) of the large bearing is y > x.

[0006] To achieve the above objectives, the technical solution adopted by this invention is: an equivalent calculation method for the friction coefficient between rolling bearings of the same type, specifically including the following steps:

[0007] Known test data for small bearings include: frictional forces obtained under different operating conditions, and bearing friction coefficients calculated based on the frictional force test results;

[0008] S1. Calculate the total contact deformation area between the rolling elements and raceway of the small bearing and the large bearing of the same type under the same working conditions. Based on the total deformation area, obtain the relationship between the force and the contact area of ​​the small bearing and the large bearing and draw their respective curves.

[0009] S2. Determine the force on the large bearing based on the force-contact area curve of the large bearing, and obtain the contact area of ​​the large bearing through force calculation; the contact area of ​​the large bearing is equivalent to the contact area of ​​the small bearing.

[0010] S3. Determine the force on the small bearing based on the force-contact area curve of the small bearing, and obtain the force-to-friction curve of the small bearing and the corresponding test friction force through the force on the small bearing; obtain the net change friction force of the small bearing through the force-to-friction curve of the small bearing and plot the net change friction force curve of the small bearing; the net change friction force of the small bearing is equivalent to the net change friction force of the large bearing.

[0011] S4. By experimenting with the no-load rotational friction of the large bearing, the no-load rotational friction of the large bearing is added to the net variable friction of the large bearing to obtain the comprehensive rotational friction of the large bearing, and the comprehensive rotational friction-axial force curve of the large bearing is plotted.

[0012] S5. Divide the total rotational friction force of the large bearing by the bearing force to obtain the total friction coefficient of the large bearing, and plot the curve of the total friction coefficient of the large bearing versus the axial force.

[0013] S6. By smoothing and extending the curves of comprehensive rotational friction force-axial force and comprehensive friction coefficient-axial force of large bearings through curve fitting and extension, the comprehensive rotational friction coefficient and comprehensive rotational friction force of large bearings under different force conditions are obtained, thereby obtaining the relevant parameters of large bearings under various working conditions.

[0014] Furthermore, in step S1, the total area of ​​contact deformation between the rolling elements and the raceway of the small bearing and the large bearing of the same type under the same working conditions is calculated by Romax software or other similar software using known algorithms.

[0015] Furthermore, in step S5, the bearing is subjected to a single force, which is either axial force or radial force.

[0016] Furthermore, in step S3, the net change friction force curve of the small bearing is obtained by translating the small bearing force and the corresponding test friction force curve along the vertical axis to pass through the origin; the purpose of this is to remove interference, remove the friction resistance caused by bearing seals, lubrication and other factors, and only retain the friction resistance generated by the deformation under force.

[0017] Furthermore, in step S4, the test friction force in the curve of the small bearing force and the corresponding test friction force is the comprehensive rotational friction force, because the test friction force incorporates all factors that cause friction force; the comprehensive rotational friction force is divided by the bearing force to obtain the comprehensive friction coefficient, and the small bearing friction coefficient-axial force curve is plotted.

[0018] The technical advantage of this invention is that it can deduce the friction coefficient of a large bearing of the same type by using the equivalent analysis method based on the friction coefficient of a small bearing of the same type. The technical principle of this method is to use the measured data of the rotational friction coefficient of a small bearing of the same type and transfer it by calculating the contact deformation area between the rolling element and the raceway to obtain the rotational friction coefficient of the large bearing. This effectively solves the technical problem that the friction coefficient of large bearings is difficult to measure. Attached Figure Description

[0019] Figure 1 This is a simplified diagram illustrating the steps of the equivalent calculation method for the friction coefficient between rolling bearings of the same type according to the present invention.

[0020] Figure 2 This is a graph showing the force and contact area of ​​small and large bearings.

[0021] Figure 3 The graph shows the curves of the force on the small bearing versus the corresponding test friction force and the curve of the net change in friction force of the small bearing.

[0022] Figure 4 This is a graph showing the friction coefficient of a small bearing versus its axial force.

[0023] Figure 5 The graphs show the combined rotational friction force-axial force curve and the combined friction coefficient-axial force curve of a large bearing (taking the case of a large bearing subjected to a 100kN axial force as an example).

[0024] Figure 6 Table 1 shows the test data of friction force for a three-row column bearing with a pitch circle diameter of 3m.

[0025] Figure 7 Table 2 shows the data for calculating the contact area of ​​a three-row column bearing with a pitch circle diameter of 3m and a pitch circle diameter of 10m.

[0026] Figure 8 Table 3 shows the comprehensive friction coefficient of small bearings.

[0027] Figure 9 Table 4 shows the comprehensive friction coefficient of the large bearing (under the condition of the large bearing being subjected to an axial force of 100kN). Detailed Implementation

[0028] To make the above-mentioned objects, features, and advantages of the present invention more apparent and understandable, specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings. Many specific details are set forth in the following description to provide a thorough understanding of the present invention. However, the present invention can be practiced in many other ways different from those described herein, and those skilled in the art can make similar modifications without departing from the spirit of the present invention. Therefore, the present invention is not limited to the specific embodiments disclosed below.

[0029] like Figure 1-8 The method for equivalent calculation of the friction coefficient between rolling bearings of the same type, as shown, specifically includes the following steps:

[0030] Known test data for small bearings include: frictional forces obtained under different operating conditions, and bearing friction coefficients calculated based on the frictional force test results;

[0031] The equivalent transition parameters are established in the following steps;

[0032] S1. Calculate the total contact deformation area between the rolling elements and raceway of the small bearing and the large bearing of the same type under the same working conditions. Based on the total deformation area, obtain the relationship between the force and contact area of ​​the small and large bearings and plot their respective curves, namely curve 1 and curve 2. Figure 1 As shown;

[0033] S2. Determine the force on the large bearing based on the force-contact area curve of the large bearing, and obtain the contact area of ​​the large bearing through force calculation; the contact area of ​​the large bearing is equivalent to the contact area of ​​the small bearing.

[0034] S3. Determine the force on the small bearing based on the force-contact area curve of the small bearing, and obtain the force-corresponding friction force curve of the small bearing from the force on the small bearing, curve 3, as shown in Figure 3. Figure 3 As shown in Figure 5, the net change in friction force of the small bearing is obtained by comparing the force applied to the small bearing with the corresponding test friction force curve, and the net change in friction force curve of the small bearing is plotted. Figure 3 As shown; the net change in friction of the small bearing is equivalent to the net change in friction of the large bearing;

[0035] S4. By experimenting with the no-load rotational friction of a large bearing, the no-load rotational friction of the large bearing is added to the net changed friction of the large bearing to obtain the comprehensive rotational friction of the large bearing. The comprehensive rotational friction-axial force curve of the large bearing is then plotted, as shown in curve 6. Figure 5 As shown;

[0036] S5. Divide the total rotational friction force of the large bearing by the bearing force to obtain the total friction coefficient of the large bearing, and plot the total friction coefficient-axial force curve of the large bearing, curve 7, as shown. Figure 5 As shown;

[0037] S6. By using curve fitting and extension, the curves of comprehensive rotational friction force-axial force of large bearings (Curve 6) and comprehensive friction coefficient-axial force of large bearings (Curve 7) are smoothed and extended to obtain the comprehensive rotational friction coefficient and comprehensive rotational friction force of large bearings under different force conditions, thereby obtaining the relevant parameters of large bearings under various working conditions.

[0038] In step S3 above, the net change friction force curve of the small bearing, curve 5, is obtained by shifting the small bearing force and the corresponding test friction force curve, curve 3, along the vertical axis to pass through the origin; the purpose of this is to remove interference, remove the friction resistance caused by bearing seals, lubrication and other factors, and only retain the friction resistance generated by the deformation under force.

[0039] In step S4, the force on the small bearing and the test friction force in the corresponding test friction force curve 3 are the comprehensive rotational friction force, because the test friction force incorporates all factors that cause friction. Dividing the comprehensive rotational friction force by the bearing force yields the comprehensive friction coefficient, and the small bearing friction coefficient-axial force curve, curve 4, is plotted. Figure 4 As shown.

[0040] The actual calculation case using the above scheme is an example of a three-row column bearing subjected to axial force.

[0041] Test data for a three-row spur bearing with a pitch circle diameter of 3m are shown in Table 1. Figure 6 As shown;

[0042] The calculated contact areas of three-row column bearings with a pitch circle diameter of 3m and 10m are shown in Table 2. Figure 7 As shown; the calculation of the comprehensive friction coefficient of the small bearing is shown in Table 3. Figure 8 As shown; (the comprehensive rotational friction force of the large bearing under no load, as tested, is 32500N). By comparing the contact area of ​​the large and small bearings under corresponding loads, the net change in friction force caused by deformation of the large bearing is obtained. Adding this to the comprehensive rotational friction force of the large bearing under no-load conditions yields the comprehensive rotational friction force of the large bearing under relevant loads. Simply increasing the load range of the small bearing provides the comprehensive rotational friction force of the large bearing under the corresponding axial force. Interpolation is then used to obtain the comprehensive rotational friction force of the entire large bearing under the corresponding axial force. Dividing this by the corresponding axial force of the large bearing yields the comprehensive friction coefficient.

[0043] It should be noted that this case only lists the case where the large bearing is subjected to an axial force of 100kN, as shown in Table 4. Figure 9 ).

[0044] Curves 1 to 5 in this case study can be found here. Figures 2 to 4 Since this case only lists the case of the large bearing subjected to an axial force of 100kN, curves 6 and 7 only provide one point, see... Figure 5 .

[0045] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0046] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0047] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0048] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "over," and "on top" of the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0049] It should be noted that when an element is referred to as being "fixed to" or "set on" another element, it can be directly on the other element or there may be an intervening element. When an element is considered to be "connected to" another element, it can be directly connected to the other element or there may be an intervening element. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used herein are for illustrative purposes only and do not represent the only possible implementation.

[0050] The above examples are merely preferred embodiments of the present invention. Obviously, the present invention is not limited to the above embodiments, and many variations are possible. All variations that can be directly derived or conceived by those skilled in the art from the disclosure of the present invention should be considered within the scope of protection of the present invention.

Claims

1. A method for equivalent calculation of the friction coefficient between rolling bearings of the same type, characterized in that, Specifically, the steps include the following: Known test data for small bearings include: frictional forces obtained under different operating conditions, and bearing friction coefficients calculated based on the frictional force test results; S1. Calculate the total contact deformation area between the rolling elements and raceway of the small bearing and the large bearing of the same type under the same working conditions. Based on the total deformation area, obtain the relationship between the force and the contact area of ​​the small bearing and the large bearing and draw their respective curves. S2. Determine the force on the large bearing based on the force-contact area curve of the large bearing, and obtain the contact area of ​​the large bearing through force calculation; the contact area of ​​the large bearing is equivalent to the contact area of ​​the small bearing. S3. Determine the force on the small bearing based on the force-contact area curve of the small bearing, and obtain the force-to-friction curve of the small bearing and the corresponding test friction force through the force on the small bearing; obtain the net change friction force of the small bearing through the force-to-friction curve of the small bearing and plot the net change friction force curve of the small bearing; the net change friction force of the small bearing is equivalent to the net change friction force of the large bearing. S4. The no-load rotational friction force of the large bearing is obtained through experiments. The no-load rotational friction force of the large bearing is added to the net variable friction force of the large bearing to obtain the comprehensive rotational friction force of the large bearing. The comprehensive rotational friction force-axial force curve of the large bearing is plotted. S5. Divide the total rotational friction force of the large bearing by the force on the large bearing to obtain the total friction coefficient of the large bearing, and plot the curve of the total friction coefficient of the large bearing versus the axial force. S6. By smoothing and extending the curves of comprehensive rotational friction force-axial force and comprehensive friction coefficient-axial force of large bearings through curve fitting and extension, the comprehensive rotational friction coefficient and comprehensive rotational friction force of large bearings under different force conditions are obtained, thereby obtaining the relevant parameters of large bearings under various working conditions.

2. The method for equivalent calculation of the friction coefficient between rolling bearings of the same type according to claim 1, characterized in that: In step S3, the net change friction curve of the small bearing is obtained by translating the force on the small bearing and the corresponding test friction curve along the vertical axis to pass through the origin.

3. The method for equivalent calculation of the friction coefficient between rolling bearings of the same type according to claim 1, characterized in that: In step S4, the force on the small bearing and the test friction force in the corresponding test friction force curve are the comprehensive rotational friction force; the comprehensive rotational friction force is divided by the force on the small bearing to obtain the comprehensive friction coefficient, and the small bearing friction coefficient-axial force curve is plotted.

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