A method for reshaping a tapered roller bearing

Abstract

The present invention relates to the technical field of bearing reshaping, specifically a tapered roller bearing reshaping method. The method includes establishing a tapered roller bearing model and applying actual stress conditions to the bearing. Crown values ​​are selected at equal intervals to calculate the comprehensive stress concentration factor (Kt) corresponding to different crown values ​​for the bearing's outer ring, inner ring, and rolling element. Curves are drawn showing the relationship between the crown values ​​of the inner ring, outer ring, and rolling element and Kt. An optimal range of crown values ​​for the outer ring, inner ring, and rolling element corresponding to the minimum Kt value is selected. With the minimum Kt value as the optimization goal, a surface response method is used to calculate the optimal crown reshaping parameters for the outer ring, inner ring, and rolling element. The crown reshaping parameters are then used to reshape the tapered roller bearing. The method simultaneously considers the possibility of stress concentration between the inner and outer rings and the rolling element, assigns weights for calculation, and establishes a bearing mechanical analysis model to determine the optimal crown reshaping range for the outer ring, inner ring, and rolling element, thereby optimizing the final bearing reshaping effect.

Description

Technical Field

[0001] The present invention relates to the technical field of bearing reshaping, and in particular to a reshaping method for a tapered roller bearing. Background Art

[0002] Conventional reshaping methods for tapered roller bearings involve rolling element crowning or end-to-end reshaping. Due to cost considerations and mounting space constraints at OEMs, requirements for bearing performance, such as load capacity and lifespan, are gradually increasing. Simply reshaping the rolling elements is no longer sufficient to meet bearing fatigue requirements. Summary of the Invention

[0003] In view of the defects of the prior art, the present invention provides a method for reshaping a tapered roller bearing. The method targets the operating conditions of the bearing, takes into account the possibility of stress concentration between the inner and outer rings of the bearing and the rolling elements, assigns weights for calculation, establishes a bearing mechanics analysis model, and obtains the optimal value range for the convexity reshaping of the outer ring, inner ring, and rolling elements of the bearing, so as to optimize the final reshaping effect of the bearing.

[0004] In order to achieve the above-mentioned object, the technical solution provided by the present invention is a method for reshaping a tapered roller bearing, the specific steps of which include:

[0005] Establish a tapered roller bearing model and load the actual bearing load conditions;

[0006] The convexity values ​​are selected at equal intervals to calculate the comprehensive stress concentration factor Kt of the bearing outer ring, inner ring and rolling element with different convexity values.

[0007] Draw the relationship curves between the inner ring convexity value and Kt, the relationship curves between the outer ring convexity value and Kt, and the relationship curves between the rolling element convexity value and Kt respectively;

[0008] Select the outer ring convexity value optimization range, inner ring convexity value optimization range and rolling element convexity value optimization range corresponding to the minimum value of Kt,

[0009] Taking the minimum Kt value as the optimization goal, the surface response method is used to calculate the optimal crowning modification parameters of the outer ring, inner ring and rolling element;

[0010] Use the crown shaping parameters to shape tapered roller bearings.

[0011] Furthermore, the shaping method further includes respectively calculating the shaping radius of the outer ring, inner ring and rolling element of the tapered roller bearing under different convexity values, and the calculation formula is:

[0012] R=[L 2 / (8×△C)]+0.5×△C,

[0013] Among them, R is the shaping radius, L is the effective length, and △C is the convexity value.

[0014] Furthermore, the step of selecting convexity values ​​at equal intervals and calculating the comprehensive stress concentration factor Kt matching different convexity values ​​of the bearing outer ring, inner ring, and rolling element includes:

[0015] The convexity values ​​are selected at equal intervals to calculate the comprehensive stress concentration factor Kt for different convexity values ​​of the bearing outer ring, inner ring, and rolling element. The calculation formula is:

[0016] Kt=A×k o + B×k i ,

[0017] in,

[0018] k o is the stress concentration factor of the outer raceway, k i is the stress concentration factor of the inner raceway, and

[0019] A and B satisfy:

[0020] A+B=1;

[0021] A / B=M / N;

[0022] M is the average contact stress between the rolling element and the outer raceway with the maximum force in the unmodified structure;

[0023] N is the average contact stress between the rolling element and the inner raceway with the maximum force in the unmodified structure;

[0024] k o is the ratio of the maximum contact stress of the outer raceway to the average contact stress of the outer raceway;

[0025] k i It is the ratio of the maximum contact stress of the inner raceway to the average contact stress of the inner raceway.

[0026] Furthermore, the outer raceway, inner raceway and rolling elements of the bearing are not modified, and the contact stress calculation results of the bearing without modification are obtained;

[0027] Based on the calculation results, the maximum outer raceway contact stress value of the rolling element with the largest force is obtained. The angular position of the rolling element with the largest force in the circumferential direction is located, and the contact stress distribution value along the generatrix of the rolling element at this angular position is obtained. The average of these values ​​is the average contact stress M between the rolling element with the largest force and the outer raceway of the unmodified structure.

[0028] Based on the calculation results, the maximum inner raceway contact stress value of the rolling element with the largest force is obtained, the angular position of the rolling element with the largest force in the circumferential direction is located, and the contact stress distribution value along the rolling element generatrix at this angular position is obtained. The average of these values ​​is the average contact stress N between the rolling element with the largest force and the inner raceway of the unmodified structure.

[0029] Furthermore, a set of convexity values ​​is selected to modify the outer and inner raceways and rolling elements of the bearing, and the contact stress calculation results of the modified bearing are obtained;

[0030] According to the calculation results, the maximum outer raceway contact stress value of the rolling element with the largest force is obtained. The angular position of the rolling element with the largest force in the circumferential direction is located, and the contact stress distribution value along the rolling element generatrix at this angular position is obtained. The average of these values ​​is the average contact stress of the outer raceway. Then, the maximum contact stress value of the outer raceway is divided by the average contact stress of the outer raceway to obtain k o ;

[0031] Based on the calculation results, the maximum inner raceway contact stress value of the rolling element with the largest force is obtained. The angular position of the rolling element with the largest force in the circumferential direction is located, and the contact stress distribution value along the generatrix of the rolling element at this angular position is obtained. The average of these values ​​is the average contact stress of the inner raceway. Then, the maximum contact stress value of the inner raceway is divided by the average contact stress of the inner raceway to obtain k i .

[0032] Furthermore, the step of selecting the outer ring convexity value optimization range, the inner ring convexity value optimization range, and the rolling element convexity value optimization range corresponding to the minimum value of Kt includes:

[0033] Select the outer ring convexity value △C corresponding to the minimum value of Kt o1 、Inner ring convexity value △C i1 And the rolling element convexity value △C1;

[0034] Calculate the outer ring convexity value △C o1 Compared with other outer ring convexity values ​​△C o The absolute value of the difference between the two outer ring convexity values ​​△C with the smaller absolute value is selected o As the convexity value △C o2 and △C o3 ;

[0035] Calculate the inner ring convexity value △C i1 Compared with other inner ring convexity values ​​△C i The absolute value of the difference between the two inner ring convex values ​​△C with the smaller absolute value is selected i As the convexity value △C i2 and △C i3 ;

[0036] Calculate the absolute value of the difference between the rolling element convexity value △C1 and the convexity values ​​△C of other rolling elements, and select the two rolling element convexity values ​​△C with the smaller absolute value as the convexity values ​​△C2 and △C3;

[0037] △C o1 , △C o2 , △C o3 , △C i1 , △Ci2 , △C i3 A total of 9 convexity values ​​including △C1, △C2 and △C3 are combined into 27 groups of convexity value combinations, and the Kt corresponding to the 27 groups of convexity value combinations are obtained respectively.

[0038] Furthermore, the tapered roller bearing model is established using Romax simulation software.

[0039] Furthermore, the tapered roller bearing model uses a stiffness bearing fit to establish a shaft system.

[0040] The beneficial effects of the present invention are as follows: with respect to the operating conditions of the bearing, the possibility of stress concentration occurring between the inner ring and outer ring of the bearing and the rolling element is considered at the same time, and weights are assigned for calculation, which can be used as an indicator for scientifically and quantitatively evaluating the anti-fatigue characteristics of the bearing; taking into account factors such as processing cost and processing feasibility, a bearing mechanics analysis model is established, and the optimal value range of the convexity modification of the bearing outer ring, inner ring, and rolling element is obtained. Taking the proposed comprehensive stress concentration coefficient as the optimization target, the surface response method is used to obtain the optimal solution for the three-convex modification. BRIEF DESCRIPTION OF THE DRAWINGS

[0041] Figure 1 Schematic diagram of the structure of a tapered roller bearing in one embodiment of the present invention;

[0042] Figure 2 Schematic diagram of the structure of the outer ring of a tapered roller bearing in one embodiment of the present invention;

[0043] Figure 3 Schematic diagram of the structure of the inner ring of a tapered roller bearing in one embodiment of the present invention;

[0044] Figure 4 Schematic diagram of the structure of the rolling element of a tapered roller bearing in one embodiment of the present invention;

[0045] Figure 5 A model established using Romax in a tapered roller bearing modification method according to one embodiment of the present invention;

[0046] Figure 6 1 is a curve showing the change of the comprehensive stress concentration factor Kt with the outer ring convexity value in a tapered roller bearing modification method in one embodiment of the present invention;

[0047] Figure 7 1 is a curve showing the change of the comprehensive stress concentration factor Kt with the convexity value of the inner ring in a tapered roller bearing modification method in one embodiment of the present invention;

[0048] Figure 8 1 is a curve showing the variation of the comprehensive stress concentration factor Kt with the convexity value of the rolling element in a tapered roller bearing modification method in one embodiment of the present invention;

[0049] In the figure: 1. Outer ring, 2. Cage, 3. Inner ring, 4. Rolling elements. DETAILED DESCRIPTION

[0050] To make the above-mentioned objects, features, and advantages of the present invention more readily apparent, specific embodiments of the present invention are described in detail below with reference to the accompanying drawings. The following description sets forth numerous specific details to facilitate a full understanding of the present invention. However, the present invention can be implemented in many other ways than those described herein, and those skilled in the art may make similar modifications without departing from the scope of the present invention. Therefore, the present invention is not limited to the specific embodiments disclosed below.

[0051] See also Figure 1 , shows a schematic diagram of the structure of a tapered roller bearing in one embodiment of the present invention, specifically a 32028 bearing, a single-row tapered roller bearing (model 32000), branded as ZWZ Bearing. The tapered roller bearing includes an outer ring 1, a cage 2, an inner ring 3, and rolling elements 4. The specific steps of the tapered roller bearing reshaping method in this embodiment include:

[0052] Step S100: Figure 5 As shown, Romax is used to establish a tapered roller bearing model and load the actual bearing load conditions; a stiffness bearing is used to establish a shaft system to avoid interference from other bearings on the analyzed bearing;

[0053] Step S200, see Figure 2-Figure 4 , calculate the trim radius of the outer ring, inner ring and rolling element of the tapered roller bearing under different convexity values ​​respectively, the calculation formula is:

[0054] R=[L 2 / (8×△C)]+0.5×△C,

[0055] Wherein, R is the trim radius, L is the effective length, and △C is the convexity value; the trim radius of the outer ring, inner ring, and rolling element of the tapered roller bearing under different convexity values ​​is calculated, and the trim radius is used as the input value for calculating the contact stress by the Romax software. After the tapered roller bearing model established in step S100 is trimmed using the calculated trim radius, the actual stress condition of the bearing is simulated to perform stress analysis, and the stress value is further obtained. Figure 4 Where r is the nominal value of the rolling element chamfer. When the formula is used to calculate the effective length of the rolling element, the effective length L in the formula is equal to the total length of the rolling element minus twice the nominal value of the rolling element chamfer.

[0056] Step S300, see Figure 6-Figure 8Considering the feasibility of processing, the contact stress distribution of the outer ring, inner ring and rolling element under the 0-40μm crown value modification is calculated. Specifically, the crown value is selected at intervals of 5μm, and the comprehensive stress concentration factor Kt of the bearing outer ring, inner ring and rolling element with different crown values ​​is calculated respectively. The calculation formula is:

[0057] Kt=A×k o + B×k i ,

[0058] in,

[0059] k o is the stress concentration factor of the outer raceway, k i is the stress concentration factor of the inner raceway, and

[0060] A and B satisfy:

[0061] A+B=1;

[0062] A / B=M / N;

[0063] M is the average contact stress between the rolling element and the outer raceway with the maximum force in the unmodified structure;

[0064] N is the average contact stress between the rolling element and the inner raceway with the maximum force in the unmodified structure;

[0065] Specifically, in one embodiment, in step S100, Romax software is used to establish a tapered roller bearing model and simulate actual load conditions. In step S300, the outer raceway, inner raceway and rolling element of the bearing are not modified, and the contact stress calculation results of the unmodified bearing are obtained. According to the calculation results, the maximum contact stress values ​​of the outer and inner raceways of the rolling element with the greatest force are obtained, the angular position of the rolling element with the greatest force in the circumferential direction is located, and the contact stress distribution value along the generatrix of the rolling element at this angular position is obtained. The average of these values ​​is the average contact stress between the rolling element with the greatest force in the unmodified structure and the outer and inner raceways. It should be noted that the average contact stress between the rolling element with the greatest force in the unmodified structure and the outer raceway refers to the average contact stress between the unmodified rolling element and the unmodified outer raceway; similarly, the average contact stress between the rolling element with the greatest force in the unmodified structure and the inner raceway refers to the average contact stress between the unmodified rolling element and the unmodified inner raceway.

[0066] k o is the ratio of the maximum contact stress of the outer raceway to the average contact stress of the outer raceway;

[0067] k i is the ratio of the maximum contact stress of the inner raceway to the average contact stress of the inner raceway;

[0068] Specifically, in one embodiment, Romax software is used to establish a tapered roller bearing model and simulate actual load conditions. A set of convexity values ​​is selected to modify the outer and inner raceways and rolling elements of the bearing to obtain the contact stress calculation results of the modified bearing. Based on the calculation results, the maximum outer raceway contact stress value of the rolling element with the greatest force is obtained, and the angular position of the rolling element with the greatest force in the circumferential direction is located to obtain the contact stress distribution value along the rolling element generatrix at this angular position. The average of these values ​​is the average contact stress of the outer raceway. Then, the maximum contact stress value of the outer raceway is divided by the average contact stress of the outer raceway to obtain k o ;

[0069] In addition, based on the calculation results, the maximum inner raceway contact stress value of the rolling element with the greatest force is obtained. The angular position of the rolling element with the greatest force in the circumferential direction is located, and the contact stress distribution value along the rolling element generatrix at this angular position is obtained. The average of these values ​​is the average contact stress of the inner raceway. Then, the maximum contact stress value of the inner raceway is divided by the average contact stress of the inner raceway to obtain k i .

[0070] Step S400, respectively draw the relationship curve between the inner ring convexity value and Kt, the relationship curve between the outer ring convexity value and Kt, and the relationship curve between the rolling element convexity value and Kt;

[0071] See also Figure 6 , select the outer ring convexity value of 40 um corresponding to the minimum Kt value; in addition, among the other outer ring convexity values, select the two convexity values ​​of 30 um and 35 um with the smaller absolute value of the difference from the outer ring convexity value of 40 um.

[0072] See also Figure 7 , select the inner ring convexity value of 20 um corresponding to the minimum Kt value; in addition, among the other inner ring convexity values, select the two convexity values ​​15 um and 25 um with the smaller absolute value of the difference from the inner ring convexity value of 20 um.

[0073] See also Figure 8 , select the rolling element convexity value of 40 um corresponding to the minimum Kt value; in addition, select the two convexity values ​​of 30 um and 35 um with the smaller absolute value of the difference from the rolling element convexity value of 40 um from other rolling element convexity values.

[0074] It should be noted that when taking the value, two relatively adjacent values ​​are taken. Specifically, when the convexity value corresponding to the minimum value of Kt is already the maximum value, the two values ​​before it are taken. When the convexity value corresponding to the minimum value of Kt is not the maximum value, the two values ​​before and after it are taken respectively.

[0075] Step S500: Figure 6-8It can be seen that the optimal range for the comprehensive stress concentration factor Kt is 30 μm to 40 μm for the outer ring crown, 30 μm to 40 μm for the rolling element crown, and 15 μm to 25 μm for the inner ring crown. See Table 1: Response table for the three-variable design, where -1 represents the minimum value of the crown optimization range, 0 represents the middle value, and 1 represents the maximum value. For example, for rolling elements, the optimal range for crown is 30 μm to 40 μm. In the response table, -1 represents 30 μm, 0 represents 35 μm, and 1 represents 40 μm.

[0076] Table 1

[0077]

[0078] According to Table 1, the surface response method can be used to calculate the outer ring, inner ring, and rolling element convexity values ​​corresponding to the optimal solution of Kt. The outer ring convexity value is 32.26μm, the inner ring convexity value is 19.64μm, and the rolling element convexity value is 35.67μm.

[0079] Step S600: Use the convexity modification parameters to modify the tapered roller bearing with an outer ring convexity value of 32.26 μm, an inner ring convexity value of 19.64 μm, and a rolling element convexity value of 35.67 μm.

[0080] Traditional empirical rolling element full convex modification formula:

[0081]

[0082] in:

[0083] △C is the convexity value, unit is mm;

[0084] L is the effective length, in mm;

[0085] E 1. E 2 is the elastic modulus of the material, in N / mm 2 ;For steel bearings ;

[0086] v 1. v 2 is the Poisson's ratio of the material. For steel bearings ;

[0087] Q is the maximum rolling element load in the bearing, measured in N.

[0088] The convexity of the outer and inner raceways is in accordance with the factory processing standards, and the convexity is generally controlled to be 3~7um.

[0089] Table 2

[0090]

[0091] See Table 2: Comparison of the optimized bearing's comprehensive stress concentration factor (Kt) with the Kt of conventional empirically designed three-lobed profiles. The optimized bearing's comprehensive stress concentration factor (Kt) is 19.58% lower than that of conventional empirically designed three-lobed profiles. This effectively alleviates bearing raceway fatigue, as verified by bearing life enhancement tests. This research result effectively improves the empirically based three-lobed profile method for bearings and has significant engineering application value.

[0092] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like to indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present invention.

[0093] 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 the technical features being referred to. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of the present invention, "plurality" means at least two, such as two, three, etc., unless otherwise specifically defined.

[0094] In the present invention, unless otherwise specified or limited, the terms "installed," "connected," "connect," "fixed," etc. should be understood in a broad sense. For example, they can refer to fixed connection, detachable connection, or integration; mechanical connection, electrical connection; direct connection, or indirect connection through an intermediate medium; internal communication between two components, or interaction between two components, unless otherwise specified. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on specific circumstances.

[0095] In the present invention, unless otherwise expressly specified or limited, when a first feature is "above" or "below" a second feature, it may mean that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediary. Furthermore, when a first feature is "above," "above," or "above" a second feature, it may mean that the first feature is directly above or diagonally above the second feature, or simply means that the first feature is at a higher level than the second feature. When a first feature is "below," "below," or "below" a second feature, it may mean that the first feature is directly below or diagonally below the second feature, or simply means that the first feature is at a lower level than the second feature.

[0096] It should be noted that when an element is referred to as being "fixed to" or "disposed on" another element, it may be directly on the other element or there may be an intermediate element. When an element is considered to be "connected to" another element, it may be directly connected to the other element or there may be an intermediate 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 implementation methods.

Claims

1. A method for reshaping a tapered roller bearing, characterized in that: The specific steps include: Establish a tapered roller bearing model and load the actual bearing load conditions; The convexity values ​​are selected at equal intervals to calculate the comprehensive stress concentration factor Kt of the bearing outer ring, inner ring and rolling element with different convexity values. Draw the relationship curves between the inner ring convexity value and Kt, the relationship curves between the outer ring convexity value and Kt, and the relationship curves between the rolling element convexity value and Kt respectively; Select the outer ring convexity value optimization range, inner ring convexity value optimization range and rolling element convexity value optimization range corresponding to the minimum value of Kt, Taking the minimum Kt value as the optimization goal, the surface response method is used to calculate the optimal crowning modification parameters of the outer ring, inner ring and rolling element; Use crown shaping parameters to shape tapered roller bearings; The step of selecting convexity values ​​at equal intervals and calculating the comprehensive stress concentration factor Kt matching different convexity values ​​of the bearing outer ring, inner ring, and rolling element comprises: The convexity values ​​are selected at equal intervals to calculate the comprehensive stress concentration factor Kt for different convexity values ​​of the bearing outer ring, inner ring, and rolling element. The calculation formula is: Kt=A×k o + B×k i , in, k o is the stress concentration factor of the outer raceway, k i is the stress concentration factor of the inner raceway, and A and B satisfy: A+B=1; A / B=M / N; M is the average contact stress between the rolling element and the outer raceway with the maximum force in the unmodified structure; N is the average contact stress between the rolling element and the inner raceway with the maximum force in the unmodified structure; The outer raceway, inner raceway and rolling elements of the bearing are not modified, and the contact stress calculation results of the bearing without modification are obtained; Based on the calculation results, the maximum outer raceway contact stress value of the rolling element with the largest force is obtained. The angular position of the rolling element with the largest force in the circumferential direction is located, and the contact stress distribution value along the generatrix of the rolling element at this angular position is obtained. The average of these values ​​is the average contact stress M between the rolling element with the largest force and the outer raceway of the unmodified structure. Based on the calculation results, the maximum inner raceway contact stress value of the rolling element with the largest force is obtained. The angular position of the rolling element with the largest force in the circumferential direction is located, and the contact stress distribution value along the generatrix of the rolling element at this angular position is obtained. The average of these values ​​is the average contact stress N between the rolling element with the largest force and the inner raceway of the unmodified structure. Select a set of convexity values ​​to modify the outer and inner raceways and rolling elements of the bearing, and obtain the contact stress calculation results of the modified bearing; According to the calculation results, the maximum outer raceway contact stress value of the rolling element with the largest force is obtained. The angular position of the rolling element with the largest force in the circumferential direction is located, and the contact stress distribution value along the rolling element generatrix at this angular position is obtained. The average of these values ​​is the average contact stress of the outer raceway. Then, the maximum contact stress value of the outer raceway is divided by the average contact stress of the outer raceway to obtain k o ; Based on the calculation results, the maximum inner raceway contact stress value of the rolling element with the largest force is obtained. The angular position of the rolling element with the largest force in the circumferential direction is located, and the contact stress distribution value along the generatrix of the rolling element at this angular position is obtained. The average of these values ​​is the average contact stress of the inner raceway. Then, the maximum contact stress value of the inner raceway is divided by the average contact stress of the inner raceway to obtain k i .

2. The method for reshaping a tapered roller bearing according to claim 1, wherein: The shaping method further includes calculating the shaping radius of the outer ring, inner ring and rolling element of the tapered roller bearing under different convexity values, and the calculation formula is: R=[L 2 / (8×△C)]+0.5×△C, Among them, R is the shaping radius, L is the effective length, and △C is the convexity value.

3. The method for reshaping a tapered roller bearing according to claim 1, wherein: The step of selecting the outer ring convexity value optimization range, the inner ring convexity value optimization range, and the rolling element convexity value optimization range corresponding to the minimum value of Kt includes: Select the outer ring convexity value △C corresponding to the minimum value of Kt o1 、Inner ring convexity value △C i1 And the rolling element convexity value △C1; Calculate the outer ring convexity value △C o1 Compared with other outer ring convexity values ​​△C o The absolute value of the difference between the two outer ring convexity values ​​△C with the smaller absolute value is selected o As the convexity value △C o2 and △C o3 ; Calculate the inner ring convexity value △C i1 Compared with other inner ring convexity values ​​△C i The absolute value of the difference between the two inner ring convexity values ​​△C with the smaller absolute value is selected i As the convexity value △C i2 and △C i3 ; Calculate the absolute value of the difference between the rolling element convexity value △C1 and the convexity values ​​△C of other rolling elements, and select the two rolling element convexity values ​​△C with the smaller absolute value as the convexity values ​​△C2 and △C3; △C o1 , △C o2 , △C o3 , △C i1 , △C i2 , △C i3 A total of 9 convexity values ​​including △C1, △C2 and △C3 are combined into 27 groups of convexity value combinations, and the Kt corresponding to the 27 groups of convexity value combinations are obtained respectively.

4. A method for reshaping a tapered roller bearing according to any one of claims 1 to 3, characterized in that: The tapered roller bearing model is established using Romax simulation software.

5. A tapered roller bearing reshaping method according to any one of claims 1 to 3, characterized in that: The tapered roller bearing model uses a stiff bearing fit to establish the shafting.

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