A method for determining the modification amount of rollers in a tapered roller bearing

Abstract

The present invention relates to a method for determining the modification amount of rollers in a tapered roller bearing, belonging to the technical field of bearings. The method of the present invention is to obtain the initial raceway radius amount of each slice corresponding to the slicing of the inner raceway of the tapered roller bearing along the horizontal length of the raceway and the shape equation of the inner raceway; determine the radial expansion amount of each slice of the raceway by using the raceway radius determined on the basis of the initial raceway radius amount of each slice and the interference amount of the raceway in the working condition of the bearing; superimpose the difference between the radial deformation amount containing the radial expansion amount of each slice of the raceway and the minimum value of the radial deformation amount containing the radial expansion amount of the raceway on the initial logarithmic modification amount to obtain the modification amount of the rollers in the tapered roller bearing.

Description

Technical Field

[0001] The present invention belongs to the technical field of bearings, and particularly relates to a method for determining the modification amount of rollers in a tapered roller bearing. Background Art

[0002] Tapered roller bearings are a type of bearing that can withstand combined loads of large axial and radial forces, and are widely used in industries such as automobiles, rolling mills, mines, metallurgy, and plastic machinery. During the long-term development of bearings, convexity modification of bearing rollers can significantly improve the bearing life. The Chinese invention patent with the application publication number CN102052398A discloses an anti-premature failure tapered roller bearing, which mentions that the bearing life can be extended through modification technology. The Chinese invention patent with the application publication number CN110502765A discloses a modification method for tapered roller bearings and a roller bearing, which mentions a modification equation that superimposes logarithmic and quadratic polynomial curves, solving the problem of limited bearing life caused by stress concentration at one end of the roller.

[0003] In the prior art, bearing modification mainly considers bearing load and bearing life, obtaining a better contact stress distribution through modification, eliminating edge stress concentration and thereby extending the bearing life. It has been relatively maturely applied in cylindrical roller bearings because the rollers and raceways of cylindrical roller bearings are both relatively regular in shape and the wall thicknesses of the raceways are equal, and the deformations at various positions of the raceway are always equal. The modification of cylindrical roller bearings can achieve better application effects. However, tapered roller bearings have a complex conical shape, and directly applying the method of cylindrical roller bearings does not achieve very ideal effects, so the modification design and processing methods of tapered roller bearings are still in development.

[0004] For tapered roller bearings, no matter which curve equation is used for modification in the prior art, it is usually defaulted that the raceway is in the initial straight state. However, in engineering practice, due to complex factors such as bearing installation and use environment, before the bearing operates, the tapered raceway will undergo minute deformations and is no longer in a straight state. When the bearing operates under load, the modification based on the straight state of the raceway does not consider the possible deformations, which may lead to a situation where the modified tapered rollers still do not match the raceway of the tapered roller bearing. Summary of the Invention

[0005] The purpose of the present invention is to provide a method for determining the modification amount of rollers in a tapered roller bearing, so as to solve the problem in the prior art that when modifying the bearing, it is defaulted that the raceway is in the initial straight state without considering the deformation of the raceway, resulting in poor modification effects and still not matching the raceway of the tapered roller bearing after modification.

[0006] To solve the above technical problems, the present invention provides a method for determining the modification amount of rollers in a tapered roller bearing, including the following steps: obtaining the initial raceway radius amount of each slice according to each slice corresponding to the horizontal length division of the inner ring raceway of the tapered roller bearing and the shape equation of the inner ring raceway; determining the radial expansion amount of the raceway of each slice by using the raceway radius determined on the basis of the initial raceway radius amount of each slice and the interference amount of the rings under the working conditions of the bearing; superimposing the difference between the radial deformation amount containing the radial expansion amount of the raceway of each slice and the minimum value of the radial deformation amounts containing the radial expansion amount of the raceway to the initial logarithmic modification amount to obtain the modification amount of the rollers in the tapered roller bearing.

[0007] Further, the radial deformation amount further includes a raceway temperature rise deformation amount;

[0008] The raceway temperature rise deformation amount of each slice under the working conditions of the bearing is determined by using the initial raceway radius amount of each slice;

[0009] The raceway radius determined on the basis of the initial raceway radius amount of each slice is updated by the raceway temperature rise deformation amount to determine the raceway radius of each slice on the basis of the initial raceway radius amount.

[0010] Further, the method for obtaining the initial raceway radius of each slice according to each slice corresponding to the horizontal length division of the inner ring raceway of the tapered roller bearing and the shape equation of the inner ring raceway includes:

[0011]

[0012] wherein, x is the axial distance in the coordinate, and y s is the raceway radius of each slice, d i is the diameter of the intersection point of the inner ring raceway and the rib surface, L is the horizontal length of the raceway, is the half cone angle of the inner ring raceway.

[0013] Further, the method for determining the raceway temperature rise deformation amount of each slice includes: determining the raceway temperature rise deformation amount of each slice under the working conditions of the bearing according to the thermal expansion coefficient of the bearing material, the raceway radius of each slice, the normal temperature and the working temperature of the bearing.

[0014] Further, the method for determining the interference amount of the rings under the working conditions of the bearing includes: determining the interference amount of the rings under the working conditions of the bearing according to the thermal expansion coefficient of the bearing material, the thermal expansion coefficient of the mating part material, the normal temperature, the working temperature of the bearing and the interference amount set at the normal temperature.

[0015] Further, the method for determining the radial expansion amount of the raceway of each slice includes: determining the radial expansion amount of the raceway of each slice according to the interference amount of the rings under the working conditions of the bearing and the raceway radius of each slice after the temperature rise deformation.

[0016] Furthermore, the temperature rise deformation of the raceways of each slice is as follows:

[0017]

[0018] In the formula, is the temperature rise deformation of the raceway of each slice, is the coefficient of thermal expansion of the bearing ring material, y s is the raceway radius of each slice, T 0 is the normal temperature of 20 °C, and T is the bearing operating temperature.

[0019] Furthermore, the interference of the bearing ring under the operating conditions of the bearing is as follows:

[0020]

[0021] In the formula, I FT is the interference of the bearing ring after the temperature rise of the raceway, is the coefficient of thermal expansion of the bearing ring material, is the coefficient of thermal expansion of the shaft material, T 0 is the normal temperature of 20 °C, T is the bearing operating temperature, I F is the interference set at normal temperature, d is the differential operator.

[0022] Furthermore, according to the interference of the bearing ring under the operating conditions of the bearing and the raceway radius of each slice after the temperature rise and deformation, the radial expansion of the raceway caused by the interference of each slice is determined by the thick-walled circular ring theoretical equation as follows:

[0023]

[0024] In the formula: is the radial expansion of the raceway caused by the interference of each slice, I FT is the interference of the bearing ring after the temperature rise of the raceway, y T is the raceway radius of each slice after the temperature rise and deformation, d is the inner diameter of the bearing, d m is the inner hole diameter of the shaft, is the Poisson's ratio of the bearing ring material, is the Poisson's ratio of the shaft material, E 1 is the elastic modulus of the bearing ring material, E 2 is the elastic modulus of the shaft material.

[0025] The beneficial effects of the above technical solution are as follows: The present invention provides a new method for determining the modification amount of rollers in a tapered roller bearing. By dividing the inner raceway of the tapered roller bearing along the horizontal length of the raceway, the inner raceway of the tapered roller bearing with uneven thickness is divided into several virtual slices, and the deformation amount of each slice is calculated independently, which is equivalent to independently studying the deformation of different positions of the tapered roller raceway. Therefore, the calculation result can be closer to the actual uneven concave and convex conditions of the tapered roller raceway at different positions. Specifically, using the interference amount of the ring under the working condition of the bearing and the initial raceway radius of each slice, the radial expansion amount of each slice of the raceway is determined. According to the radial expansion amount of each slice of its own raceway, the radial deformation amount of each slice of its own is obtained. The difference between the radial deformation amount of each slice of its own and the minimum value of the radial deformation amount including the radial expansion amount of the raceway is superimposed on the initial logarithmic modification amount to obtain the modification amount of the rollers in the tapered roller bearing. Considering the influence of the interference amount factor on the deformation of the raceway, the difference between the radial deformation amount of each slice of its own and the minimum value of the radial expansion amount is superimposed on the initial logarithmic modification amount and then the rollers are subjected to modification processing. This is equivalent to transferring the actual deformation amount corresponding to the raceway to the modification amount of the rollers in the actual state where the raceway is non-linear, so as to make the surface shape of the rollers more suitable for the actual state during the operation of the bearing, thereby effectively improving the contact stress distribution of the raceway during the operation of the bearing, making the bearing operation more stable, and ultimately improving the service life of the bearing, and solving the problem in the prior art that when modifying the bearing, the raceway is defaulted to the initial straight state without considering the deformation of the raceway, resulting in poor modification effect. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] Figure 1 is a schematic diagram of a tapered roller bearing of the method for determining the modification amount of rollers in a tapered roller bearing according to an embodiment of the method for determining the modification amount of rollers in a tapered roller bearing of the present invention;

[0027] Figure 2 is a geometric diagram of the inner ring of a tapered roller bearing of the method for determining the modification amount of rollers in a tapered roller bearing according to an embodiment of the method for determining the modification amount of rollers in a tapered roller bearing of the present invention;

[0028] Figure 3 is a diagram of the difference in deformation amount before and after modification of the inner raceway of a tapered roller of the method for determining the modification amount of rollers in a tapered roller bearing according to an embodiment of the method for determining the modification amount of rollers in a tapered roller bearing of the present invention;

[0029] Figure 4 is a comparison diagram of modification curves of the method for determining the modification amount of rollers in a tapered roller bearing according to an embodiment of the method for determining the modification amount of rollers in a tapered roller bearing of the present invention;

[0030] Figure 1Among them, 1 is the inner ring of the bearing; 1.1 is the initial raceway of the inner ring; 1.2 is the raceway after deformation; 2 is the tapered roller; 2.1 is the tapered roller after profile modification; 3 is the cage; 4 is the outer ring of the bearing; 5 is the shaft. Specific implementation manner

[0031] In order to make the objectives, technical solutions and advantages of the present invention clearer, the present invention will be further described in detail below with reference to the accompanying drawings and embodiments.

[0032] Embodiment of the method for determining the modification amount of the rollers in a tapered roller bearing:

[0033] A method for determining the modification amount of the rollers in a tapered roller bearing in this embodiment specifically is that considering the deformation of the inner ring raceway of the tapered roller bearing, the inner ring raceway of the tapered roller bearing is divided into several virtual slices by cutting along the horizontal length of the raceway. Considering the deformation influence of the interference amount factor on the raceway, the radial expansion amount of the raceway caused by the interference amount at each slice at the working temperature is calculated. According to the radial expansion amount of the raceway caused by the interference amount at each slice at the working temperature, the radial deformation amount including the radial expansion amount of the raceway is obtained. The radial deformation amount of each slice and the initial logarithmic modification amount are used to obtain the modification amount of the rollers in the tapered roller bearing. In this way, the surface shape of the rollers is made more suitable for the actual state during the operation of the bearing, thereby effectively improving the contact stress distribution of the raceway during the operation of the bearing and making the bearing operation more stable.

[0034] Then the method for determining the modification amount of the rollers in the tapered roller bearing specifically includes:

[0035] According to each slice corresponding to the cutting of the inner ring raceway of the tapered roller bearing along the horizontal length of the raceway and the shape equation of the inner ring raceway, the initial raceway radius amount of each slice is obtained; the radial expansion amount of the raceway of each slice is determined by using the raceway radius determined on the basis of the initial raceway radius amount of each slice and the interference amount of the ring during the operation of the bearing; the difference between the radial deformation amount of each slice including the radial expansion amount of the raceway and the minimum value in the radial deformation amount including the radial expansion amount of the raceway is superimposed on the initial logarithmic modification amount to obtain the modification amount of the rollers in the tapered roller bearing.

[0036] The method for determining the modification amount of the rollers in a tapered roller bearing according to this embodiment divides the inner raceway of the tapered roller bearing along the horizontal length of the raceway, divides the inner raceway of the tapered roller bearing with uneven thickness into several virtual slices, and independently calculates the deformation amount of each slice, which is equivalent to independently studying the deformation of different positions of the tapered roller raceway. Thus, the calculation result can be closer to the actual concave and convex conditions of the tapered roller raceway at different positions. Specifically, by using the interference fit amount of the raceway under the working condition of the bearing and the initial raceway radius of each slice, the radial expansion amount of each slice of the raceway is determined. According to the radial expansion amount of each slice of its own raceway, the radial deformation amount of each slice of its own is obtained. The difference between the radial deformation amount of each slice of its own and the minimum value of the radial deformation amount including the radial expansion amount of the raceway is superimposed on the initial logarithmic modification amount to obtain the modification amount of the rollers in the tapered roller bearing. Considering the influence of the interference fit amount factor on the deformation of the raceway, after the difference between the radial deformation amount of each slice of its own and the minimum value of the radial expansion amount is superimposed on the initial logarithmic modification amount and then the rollers are subjected to modification processing, it is equivalent to transferring the actual deformation amount corresponding to the raceway to the modification amount of the rollers in the actual state where the raceway is non-linear, so as to make the surface shape of the rollers more suitable for the actual state during the operation of the bearing, thereby effectively improving the contact stress distribution of the raceway during the operation of the bearing, making the bearing operation more stable, and finally increasing the service life of the bearing, and solving the problem in the prior art that when modifying the bearing, the raceway is defaulted to the initial straight state without considering the deformation of the raceway, resulting in a poor modification effect.

[0037] In this embodiment, the radial deformation amount further includes the raceway temperature rise deformation amount;

[0038] The raceway temperature rise deformation amount of each slice under the working condition of the bearing is determined by using the initial raceway radius amount of each slice;

[0039] The raceway radius of each slice determined on the basis of the initial raceway radius amount is updated by the raceway temperature rise deformation amount on the basis of the initial raceway radius amount to determine the raceway radius of each slice.

[0040] Specifically, the tapered roller bearing is usually installed on the shaft with an interference fit, and the interference fit amount will cause the inner raceway to deform; moreover, as the tapered roller bearing starts to work, its temperature rises from room temperature to the working temperature, and the temperature will also cause the inner raceway to deform; such as Figure 1As shown in the figure, 1 is the inner ring of the bearing; 1.1 is the initial raceway of the inner ring; 1.2 is the raceway after deformation; 2 is the tapered roller; 2.1 is the tapered roller after profile modification; 3 is the cage; 4 is the outer ring of the bearing; 5 is the shaft; the raceway deforms from the initial raceway 1.1 of the inner ring to the raceway 1.2 after deformation. Moreover, due to the tapered shape of the inner ring 1 of the bearing and the unequal wall thickness, the deformation amounts will also be unequal. In the current technology, the influence of deformation is not considered, and the raceway is regarded as a straight line. To eliminate the edge contact stress, the surface of the tapered roller 2 is usually profile-modified, and the profile-modified tapered roller 2.1 fits better with the raceway. The profile modification amount is generally in the micron level. Obviously, the profile modification of this magnitude cannot ignore the influence of deformation. Therefore, in this embodiment, the deformation amount of the inner ring 1 of the bearing is calculated by slicing, and in the non-straight state of the raceway, the deformation amount is transferred to the profile modification equation of the tapered roller 2 to reduce the influence of deformation on the contact stress.

[0041] To calculate the deformation amount of the raceway, the slicing method is proposed in the method for determining the profile modification amount of the rollers in the tapered roller bearing in this embodiment. In the subsequent calculations, the slices are not related to each other and the deformation amounts at different positions can be calculated separately.

[0042] Specifically, the method for obtaining the initial raceway radius of each slice according to each slice corresponding to the horizontal length of the inner ring raceway of the tapered roller bearing and the shape equation of the inner ring raceway includes:

[0043]

[0044] where x is the axial distance in the coordinate, and y s is the raceway radius of each slice, d i is the diameter of the intersection point of the inner ring raceway and the rib surface, L is the horizontal length of the raceway, is the half cone angle of the inner ring raceway.

[0045] Such as Figure 2 shown, based on the geometric parameters of the raceway, the shape equation of the inner ring raceway is established to obtain the initial raceway radius of each slice:

[0046]

[0047]

[0048] where n is the number of raceway slices.

[0049] Thus, the initial raceway radius of each slice can be obtained:

[0050]

[0051] At this time, the raceway is sliced into n pieces. Each piece is calculated separately in subsequent calculations without interference. The value of n is determined according to the bearing size and the amount of calculation.

[0052] Considering the influence of temperature and interference fit on the deformation of the raceway, calculate the temperature rise deformation of the raceway of each slice and the radial expansion of the raceway affected by the interference fit. When calculating the influence of the interference fit, since the interference fit during installation will change when the temperature rises, the calculation should be based on the interference fit after the temperature rise. Sum the two to obtain the radial deformation of each slice.

[0053] To obtain a better contact stress distribution, it is necessary to take the difference of the deformation. Set the minimum value in the radial deformation as the 0 point (i.e., the reference point), and calculate the difference between the radial deformation of each slice and the minimum value at the end of the radial deformation:

[0054]

[0055] In the formula, y L is the difference between the radial deformation of each slice and the minimum value in the radial deformation, is the radial deformation of each slice, is the minimum value in the radial deformation of each slice.

[0056] To simplify the calculation, the roller profile modification amount is composed of the initial logarithmic profile modification amount and the deformation compensation. Among them, the initial logarithmic profile modification amount is the method calculated according to the straight raceway in the prior art.

[0057] In this embodiment, the initial logarithmic profile modification amount includes the profile modification amount corresponding to the Lundberg logarithmic equation or the Johns logarithmic equation. In other embodiments, other existing initial logarithmic profile modification amounts can also be used. The specific initial logarithmic profile modification amount belongs to the prior art and will not be elaborated here.

[0058] Specifically, the initial logarithmic profile modification amount is the method calculated according to the straight raceway in the prior art. In the prior art, the Lundberg logarithmic equation or the Johns logarithmic equation is used to modify the raceway. On the basis of the Lundberg logarithmic equation or the Johns logarithmic equation, the difference between the radial deformation of each slice and the minimum value in the radial deformation is superimposed, as shown below:

[0059] y = y d + y L

[0060] In the formula, y is the profile modification amount of the roller in the tapered roller bearing, y d is the initial logarithmic profile modification amount,y L is the difference between the radial deformation of each slice and the minimum value of the radial deformations. After analysis, it is found that if the radial deformations of each slice are directly used to correct the raceway, the raceway radii of the initial slices of the raceway y s are corrected to: ( y s — ); recalculating the radial deformation of the raceway according to the corrected initial raceway radius equation of each slice will find that the radial deformations of the calculated slices have not changed. Since the values of the raceway radii of each slice are much larger than the radial deformations of each slice, the radial deformations of each slice are swallowed up during the calculation process. Taking the difference between the original deformation and the deformation calculated after the raceway correction, as Figure 3 shown, Figure 3 the ordinate is this difference, and the abscissa is the axial distance x at the coordinate. It can be seen that the difference is at the 10 -9 level and is almost 0. It can be seen that directly correcting the raceway actually cannot achieve the effect of correcting the influence of the deformation. Therefore, in this embodiment, the deformation of the raceway is corrected on the surface of the roller in contact with the raceway, which is equivalent to transferring the actual deformation amount corresponding to the raceway to the modification amount of the roller, so as to make the shape of the roller surface more suitable for the actual state during the operation of the bearing, thereby reducing the contact stress during contact.

[0061] Specifically, the difference between the radial deformation of each slice itself and the minimum value of the radial deformations is respectively superimposed on the initial logarithmic modification amount to obtain the modification amount of the roller in the tapered roller bearing.

[0062] In this embodiment, the method for determining the raceway temperature rise deformation of each slice includes: determining the raceway temperature rise deformation of each slice under the working condition of the bearing according to the thermal expansion coefficient of the bearing material, the raceway radius of each slice, the normal temperature and the working temperature of the bearing.

[0063] Specifically, the raceway temperature rise deformation of each slice is as follows:

[0064]

[0065] In the formula, is the raceway temperature rise deformation of each slice, is the thermal expansion coefficient of the bearing ring material, y s is the raceway radius of each slice, T 0 is the normal temperature of 20 °C, and T is the working temperature of the bearing.

[0066] Among them, the thermal expansion coefficient of bearing steel is generally 12×10 -5 (1 / °C).

[0067] In this embodiment, the method for determining the interference of the raceway of the bearing during operation includes: determining the interference of the raceway of the bearing during operation according to the coefficient of thermal expansion of the bearing material, the coefficient of thermal expansion of the mating part material, the normal temperature, the operating temperature of the bearing, and the interference set at normal temperature.

[0068] Specifically, the interference of the raceway of the bearing during operation is as follows:

[0069]

[0070] In the formula, I FT is the interference of the raceway after the temperature rise of the raceway, is the coefficient of thermal expansion of the bearing raceway material, is the coefficient of thermal expansion of the shaft material, T 0 is the normal temperature of 20 °C, T is the operating temperature of the bearing, I F is the interference set at normal temperature, d represents the differential operator.

[0071] In this embodiment, the method for determining the radial expansion of the raceway of each slice includes: determining the radial expansion of the raceway of each slice according to the interference of the raceway of the bearing during operation and the radius of the raceway of each slice after temperature rise and deformation.

[0072] Specifically, according to the interference of the raceway of the bearing during operation and the radius of the raceway of each slice after temperature rise and deformation, the radial expansion of the raceway caused by the interference of each slice is determined by the thick-walled circular ring theoretical equation as follows:

[0073]

[0074] In the formula: is the radial expansion of the raceway caused by the interference of each slice, I FT is the interference of the raceway after the temperature rise of the raceway, y T is the radius of the raceway of each slice after temperature rise and deformation, d is the inner diameter of the bearing, d m is the inner hole diameter of the shaft, is the Poisson's ratio of the bearing raceway material, is the Poisson's ratio of the shaft material, E 1 is the elastic modulus of the bearing raceway material, E 2 is the elastic modulus of the shaft material.

[0075] Taking a certain bearing with an inner diameter d = 150 mm, a shaft diameter of 150 mm, and a shaft hole d m = 120 mm,d i = 193.465 mm, L = 54 mm, = 12°12’30’’. Design interference I F is 0.02 mm. The initial temperature is normal temperature 20 °C, and the working temperature is 90 °C. The thermal expansion coefficient of the bearing ring material is 12.5×10 -6 ( / °C), elastic modulus E 1 = 208000 MPa, Poisson's ratio = 0.3, the thermal expansion coefficient of the shaft material is 11.7×10 -6 ( / °C), elastic modulus E 2 = 173000 MPa, Poisson's ratio = 0.3 as an example, the specific process example of the method for determining the roller profile modification amount in a tapered roller bearing in this embodiment is as follows:

[0076] Step 1: Slice the bearing ring, and calculate the raceway radius y of each slice according to the raceway shape equation s :

[0077]

[0078] In the formula, y s is the raceway radius of each slice.

[0079] Divide x by 1 mm, and divide it into 54 parts:

[0080] .

[0081] The raceway radius of each slice can be obtained:

[0082] .

[0083] Step 2: Calculate the raceway temperature rise deformation amount of each slice :

[0084]

[0085] In the formula, is the raceway temperature rise deformation amount of each slice, is the thermal expansion coefficient of the bearing ring material, y s is the raceway radius of each slice, T 0 is normal temperature 20 °C, and T is the bearing working temperature.

[0086] The raceway temperature rise deformation amount of each slice can be obtained :

[0087] .

[0088] Step 3: Update the raceway radius of the ring slice y T = y s + :[[]]

[0089] .

[0090] Step 4: Calculate the interference of the ring at the bearing operating temperature I FT :[[]]

[0091]

[0092] In the formula, I FT is the interference of the ring after the raceway temperature rise, is the thermal expansion coefficient of the bearing ring material, is the thermal expansion coefficient of the shaft material, T 0 is the normal temperature of 20 °C, T is the bearing operating temperature, I F is the set interference at normal temperature, d represents the differential operator.

[0093] Step 5: Calculate the radial expansion of the raceway caused by the interference of each slice under working conditions :[[]]

[0094]

[0095] In the formula:[[]] is the radial expansion of the raceway caused by the interference of each slice, I FT is the interference of the ring after the raceway temperature rise, y T is the raceway radius of each slice after temperature rise deformation, d is the inner diameter of the bearing, d m is the inner hole diameter of the shaft, is the Poisson's ratio of the bearing ring material, is the Poisson's ratio of the shaft material, E 1 is the elastic modulus of the bearing ring material, E 2 is the elastic modulus of the shaft material;

[0096] .

[0097] Step 6: Calculate the radial deformation of each slice :[[]]

[0098] .

[0099] Step 7: Set the minimum value in the radial deformation amount to 0, and calculate the difference between the radial deformation amount of each slice and the minimum value in the radial deformation amount:

[0100]

[0101] In the formula, y L is the difference between the radial deformation amount of each slice and the minimum value in the radial deformation amount, is the radial deformation amount of each slice, is the minimum value in the radial deformation amount of each slice;

[0102] .

[0103] Step 8: Output the profile modification amount y of the rollers in the tapered roller bearing:

[0104] y = y d + y L

[0105] In the formula, y d is the initial logarithmic profile modification amount;

[0106] .

[0107] According to the finally obtained profile modification amount, perform convexity profile modification on the roller surface.

[0108] From Figure 4 Compare the original profile modification curve and the profile modification curve obtained in this embodiment, where the ordinate is the profile modification amount y , and the abscissa is the axial distance x under the coordinate; after considering more factors, the profile modification curve obtained in this embodiment has significantly different profile modification values from the original profile modification curve and is more in line with the actual situation of the deformed raceway.

[0109] The specific implementation manners are given above, but the present invention is not limited to the described implementation manners. The basic idea of the present invention lies in the above basic solution. For those of ordinary skill in the art, according to the teachings of the present invention, designing various deformed models, formulas, and parameters does not require creative labor. Changes, modifications, substitutions, and variations made to the implementation manners without departing from the principles and spirit of the present invention still fall within the protection scope of the present invention.

Claims

1. A method for determining the roller modification amount in a tapered roller bearing, characterized in that: The method comprises the following steps: obtaining the initial raceway radius of each slice according to the slices corresponding to the horizontal length of the inner ring raceway of the tapered roller bearing and the shape equation of the inner ring raceway; adding the difference between the radial deformation of each slice and the minimum value of the radial deformation to the initial logarithmic modification amount to obtain the modification amount of the roller in the tapered roller bearing; The temperature rise deformation of the raceway of each slice under the working condition of the bearing is determined by the initial raceway radius of each slice; The radial deformation is determined according to the sum of the temperature rise deformation of the raceway and the radial expansion of the raceway; The radial expansion of the raceway determined by the thick-walled ring theory equation is as follows: Where: E I is the radial expansion of the raceway caused by the interference of each slice, FT is the interference of the ring after the raceway temperature rises, y T is the raceway radius of each slice after temperature rise deformation, d is the inner diameter of the bearing, and d m is the inner diameter of the shaft, μ1 is the Poisson's ratio of the bearing ring material, μ2 is the Poisson's ratio of the shaft material, E1 is the elastic modulus of the bearing ring material, and E2 is the elastic modulus of the shaft material; The raceway radius of each slice after temperature rise deformation is determined by superimposing the raceway temperature rise deformation amount on the initial raceway radius amount of each slice.

2. The method for determining the roller modification amount in a tapered roller bearing according to claim 1, characterized in that: Methods for obtaining the initial raceway radius of each slice according to the slices corresponding to the inner ring raceway of the tapered roller bearing cut along the horizontal length of the raceway and the shape equation of the inner ring raceway include: y s =0.5d i -(Lx)andβ In the formula, x is the axial distance under the coordinate, y is s is the initial raceway radius of each slice, d i is the diameter of the intersection of the inner ring raceway and the flange surface, L is the horizontal length of the raceway, and β is the semi-cone angle of the inner ring raceway.

3. The method for determining the roller modification amount in a tapered roller bearing according to claim 1 or 2, characterized in that: The method of determining the temperature rise deformation of the raceway of each slice includes: determining the temperature rise deformation of the raceway of each slice under the working condition of the bearing according to the thermal expansion coefficient of the bearing material, the initial raceway radius of each slice, the normal temperature and the bearing working temperature.

4. The method for determining the roller modification amount in a tapered roller bearing according to claim 1, characterized in that: Methods for determining the interference amount of the ring under the working condition of the bearing include: determining the interference amount of the ring under the working condition of the bearing according to the thermal expansion coefficient of the bearing material, the thermal expansion coefficient of the mating part material, normal temperature, the bearing working temperature and the interference amount set at normal temperature.

5. The method for determining the roller modification amount in a tapered roller bearing according to claim 3, characterized in that: The temperature rise deformation of the raceway of each slice is as follows: δ T =Γ i y s (T-T0) In the formula, δ T is the temperature rise deformation of the raceway of each slice, Γ i is the thermal expansion coefficient of the bearing ring material, y s is the initial raceway radius of each slice, T0 is the room temperature of 20℃, and T is the bearing operating temperature.

6. The method for determining the roller modification amount in a tapered roller bearing according to claim 4, characterized in that: The interference of the rings under the working condition of the bearing is as follows: I FT =(Γ i -Γ)d(T-T0)+I F In the formula, I FT is the interference of the ring after the raceway temperature rises, Γ i is the thermal expansion coefficient of the bearing ring material, Γ is the thermal expansion coefficient of the shaft material, T0 is the room temperature of 20°C, T is the bearing operating temperature, I F is the interference set at room temperature, and d is the inner diameter of the bearing.

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