Method for determining modification amount of roller in tapered roller bearing

Abstract

The invention relates to a method for determining the modification amount of a roller in a tapered roller bearing, and belongs to the technical field of bearings. The method comprises the following steps of: obtaining an initial raceway radius amount of each slice according to each slice corresponding to the inner ring raceway of the tapered roller bearing along the horizontal length of the raceway and a shape equation of the inner ring raceway; determining the radial expansion amount of the raceway of each slice by utilizing the raceway radius determined on the basis of the initial raceway radius amount of each slice and the ferrule interference amount under the working condition of the bearing; and the difference value between the radial deformation amount containing the raceway radial swelling amount of each slice and the minimum value in the radial deformation amount containing the raceway radial swelling amount is superposed to the initial logarithmic modification amount, and the modification amount of the roller in the tapered roller bearing is obtained.

Description

Technical Field

[0001] The invention belongs to the technical field of bearings, and in particular relates to a method for determining roller modification amounts in tapered roller bearings. Background Art

[0002] Tapered roller bearings are a type of bearing that can withstand large combined axial and radial force loads and are widely used in the automotive, rolling mill, mining, metallurgy, plastic machinery and other industries. In the long-term development of bearings, convex shaping of bearing rollers can greatly improve the life of bearings. The Chinese invention patent with application publication number CN102052398A discloses a tapered roller bearing that resists premature aging, which mentions that the life of the bearing can be extended through shaping technology. The Chinese invention patent with application publication number CN110502765A discloses a shaping method for tapered roller bearings and roller bearings, which mentions a shaping equation that superimposes logarithmic and quadratic polynomial curves, which solves the problem of limited bearing life caused by stress concentration at one end of the roller.

[0003] In the prior art, the main considerations for bearing modification are bearing load and bearing life. The modification is used to obtain a better contact stress distribution, eliminate edge stress concentration, and extend the bearing life. It has been used more maturely in cylindrical roller bearings because the rollers and rings of cylindrical roller bearings are of regular shape, the wall thickness of the rings is also equal, and the deformation of each position of the raceway is always equal. The modification of cylindrical roller bearings can achieve better application effects. However, tapered roller bearings have a complex tapered shape, and the method of directly applying cylindrical roller bearings cannot achieve a very ideal effect, so the modification design and processing methods of tapered roller bearings are still under development.

[0004] For tapered roller bearings, the existing technology usually assumes that the raceway is in the initial straight state regardless of which curve equation is used for shaping. However, in actual engineering, due to complex factors such as bearing installation and use environment, the tapered raceway will undergo slight deformation before the bearing is operated and is no longer in a straight state. When the bearing is running under load, the shaping of the raceway in a straight state does not take into account the possible deformation, which will result in the tapered roller still not matching the tapered roller bearing ring after shaping. Summary of the invention

[0005] The purpose of the present invention is to provide a method for determining the roller shaping amount in a tapered roller bearing, so as to solve the problem that in the prior art, when shaping the bearing, the raceway is assumed to be in an initial straight line state without considering the deformation of the raceway, resulting in poor shaping effect and still not matching the tapered roller bearing ring after shaping.

[0006] In order to solve the above technical problems, the present invention provides a method for determining the roller modification amount in a tapered roller bearing, comprising the following steps: obtaining the initial raceway radius of each slice according to the slices corresponding to the inner ring raceway of the tapered roller bearing divided along the horizontal length of the raceway and the shape equation of the inner ring raceway; determining the raceway radial expansion of each slice using the raceway radius of each slice determined on the basis of the initial raceway radius and the interference of the ring under the working condition of the bearing; adding the difference between the radial deformation of each slice including the raceway radial expansion and the minimum value of the radial deformation including the raceway radial expansion to the initial logarithmic modification amount to obtain the roller modification amount in the tapered roller bearing.

[0007] Furthermore, the radial deformation also includes the temperature rise deformation of the raceway; 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 raceway radius of each slice determined on the basis of the initial raceway radius is determined by updating the raceway radius of each slice based on the raceway temperature rise deformation.

[0008] Furthermore, the initial raceway radius of each slice is obtained 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, including: In the formula, x is the axial distance under the coordinate, y is s is the 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, is the semi-cone angle of the inner ring raceway.

[0009] Furthermore, 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 bearing working condition according to the thermal expansion coefficient of the bearing material, the raceway radius of each slice, normal temperature and the bearing working temperature.

[0010] Furthermore, the method for determining the interference amount of the ring when the bearing is working includes: determining the interference amount of the ring when the bearing is working according to the thermal expansion coefficient of the bearing material, the thermal expansion coefficient of the mating part material, normal temperature, the bearing operating temperature and the interference amount set at normal temperature.

[0011] Furthermore, the method of 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 ring under the working condition of the bearing and the raceway radius of each slice after temperature rise deformation.

[0012] Furthermore, the temperature rise deformation of the raceway of each slice is as follows: In the formula, is the temperature rise deformation of the raceway of each slice, is the thermal expansion coefficient of the bearing ring material, y s is the raceway radius of each slice, T0 is the room temperature of 20℃, and T is the bearing operating temperature.

[0013] Furthermore, the interference of the ring of the bearing under working condition is as follows: In the formula, I FT is the interference of the ferrule after the raceway temperature rises, is the thermal expansion coefficient of the bearing ring material, 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 The interference set at room temperature. d is the differential operator.

[0014] Furthermore, according to the interference of the ring under the working condition of the bearing and the raceway radius of each slice after temperature rise deformation, the radial expansion of the raceway caused by the interference of each slice is determined by the thick-walled ring theory equation as shown below: Where: 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 rises, y T is the raceway radius of each slice after temperature rise deformation, d is the bearing inner diameter, d m is the inner diameter of the shaft, is the Poisson's ratio of the bearing ring material, 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.

[0015] The beneficial effects of the above technical solution are as follows: the present invention provides a new method for determining the roller modification amount in a tapered roller bearing, by cutting the inner ring raceway of the tapered roller bearing along the horizontal length of the raceway, dividing the inner ring raceway of the tapered roller bearing with uneven thickness into several virtual slices, and independently calculating the deformation of each slice, which is equivalent to independently studying the deformation of the tapered roller raceway at different positions, thereby making the calculation result closer to the different concave and convex conditions of the tapered roller raceway at different positions. Specifically, the radial expansion of the raceway of each slice is determined by utilizing the interference of the ring under the working condition of the bearing and the initial raceway radius of each slice, and the radial deformation of each slice itself is obtained according to the radial expansion of the raceway of each slice itself, and the radial deformation of each slice itself is compared with the radial deformation including the radial expansion of the raceway. The difference between the minimum values ​​in the above formula is superimposed on the initial logarithmic modification amount to obtain the modification amount of the roller in the tapered roller bearing. The deformation effect of the interference factor on the raceway is taken into account. The difference between the minimum value in the radial deformation of each slice and the radial expansion amount is calculated and superimposed on the initial logarithmic modification amount before the roller is modified. This is equivalent to transferring the actual deformation corresponding to the raceway to the modification amount of the roller under the actual state of the raceway being non-linear, so as to make the surface shape of the roller more suitable for the actual state of the bearing during operation, thereby effectively improving the contact stress distribution of the raceway during the operation of the bearing, making the bearing run more stably, and finally improving the service life of the bearing. This solves the problem that the raceway is assumed to be in the initial straight line state when the bearing is modified in the prior art, and the deformation of the raceway is not considered, resulting in poor modification effect. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 It is a schematic diagram of a tapered roller bearing of a method for determining a roller modification amount in a tapered roller bearing according to an embodiment of the present invention; Figure 2 It is a geometric diagram of the inner ring of a tapered roller bearing of a method for determining the roller modification amount in a tapered roller bearing according to an embodiment of the present invention; Figure 3 It is a diagram showing the difference in deformation before and after the tapered roller inner ring raceway is modified in the method for determining the roller modification amount in a tapered roller bearing according to an embodiment of the present invention; Figure 4 is a modification curve comparison diagram of a method for determining a roller modification amount in a tapered roller bearing according to an embodiment of the method for determining a roller modification amount in a tapered roller bearing of the present invention; Figure 1 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 modification; 3 is the retainer; 4 is the outer ring of the bearing; and 5 is the shaft. DETAILED DESCRIPTION

[0017] In order to make the purpose, technical solutions and advantages of the present invention more clear, the present invention is further described in detail below with reference to the accompanying drawings and embodiments.

[0018] Method for determining roller modification amount in tapered roller bearings: The method of determining the roller modification amount in a tapered roller bearing of the present embodiment specifically considers the deformation of the inner ring raceway of the tapered roller bearing, divides the inner ring raceway of the tapered roller bearing into several virtual slices along the horizontal length of the raceway, considers the deformation effect of the interference factor on the raceway, calculates the radial expansion of the raceway caused by the interference at the working temperature of each slice, obtains the radial deformation including the radial expansion of the raceway according to the radial expansion of the raceway caused by the interference at the working temperature of each slice, and obtains the modification amount of the roller in the tapered roller bearing by combining the radial deformation of each slice and the initial logarithmic modification amount. In this way, the roller surface shape is more suitable for the actual state of the bearing during operation, thereby effectively improving the contact stress distribution of the raceway during the operation of the bearing, and making the bearing operation more stable.

[0019] The method for determining the roller modification amount in a tapered roller bearing specifically includes: The initial raceway radius of each slice is obtained 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; the radial expansion of the raceway of each slice is determined by using the raceway radius of each slice determined on the basis of the initial raceway radius and the interference of the ring under the working condition of the bearing; the difference between the radial deformation of each slice including the radial expansion of the raceway and the minimum value of the radial deformation including the radial expansion of the raceway is added to the initial logarithmic modification amount to obtain the modification amount of the roller in the tapered roller bearing.

[0020] The method for determining the roller modification amount in the tapered roller bearing of the present embodiment is to divide the inner ring raceway of the tapered roller bearing along the horizontal length of the raceway, divide the inner ring raceway of the tapered roller bearing with uneven thickness into several virtual slices, and independently calculate the deformation of each slice, which is equivalent to independently studying the deformation of the tapered roller raceway at different positions, thereby making the calculation result closer to the different concave and convex conditions of the tapered roller raceway at different positions. Specifically, the radial expansion of the raceway of each slice is determined by using the interference of the ring under the working condition of the bearing and the initial raceway radius of each slice, and the radial deformation of each slice itself is obtained according to the radial expansion of the raceway of each slice itself, and the difference between the radial deformation of each slice itself and the minimum value of the radial deformation including the radial expansion of the raceway is superimposed. The amount of the roller deformation is added to the initial logarithmic shaping amount to obtain the shaping amount of the roller in the tapered roller bearing, taking into account the deformation effect of the interference factor on the raceway, and the difference between the calculated radial deformation of each slice and the minimum value of the radial expansion is superimposed on the initial logarithmic shaping amount before the roller is subjected to shaping processing. This is equivalent to transferring the actual deformation corresponding to the raceway to the shaping amount of the roller under the actual state of the raceway being non-linear, so as to make the surface shape of the roller more suitable for the actual state of the bearing during operation, thereby effectively improving the contact stress distribution of the raceway during bearing operation, making the bearing operation more stable, and ultimately increasing the service life of the bearing, solving the problem that in the prior art, when the bearing is modified, the raceway is assumed to be in the initial straight line state without considering the deformation of the raceway, resulting in poor modification effect.

[0021] In this embodiment, the radial deformation also includes the raceway temperature rise deformation; 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 raceway radius of each slice determined on the basis of the initial raceway radius is determined by updating the raceway radius of each slice based on the raceway temperature rise deformation.

[0022] Specifically, tapered roller bearings are usually installed on the shaft with interference fit, and the interference fit will cause the inner ring raceway to deform. Moreover, as the tapered roller bearing starts to work, its temperature rises from room temperature to operating temperature, which will also cause the inner ring raceway to deform. Figure 1As shown, 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 modification; 3 is the retainer; 4 is the outer ring of the bearing; 5 is the shaft; the raceway is deformed from the initial raceway 1.1 of the inner ring to the deformed raceway 1.2. Moreover, due to the tapered shape of the inner ring 1 of the bearing and the different wall thicknesses, the resulting deformation amounts will also be unequal. The influence of deformation is not considered in the existing technology, and the raceway is regarded as a straight line. In order to eliminate the edge contact stress, the surface of the tapered roller 2 is usually modified, and the modified tapered roller 2.1 fits the raceway better. The modification amount is generally in the micron level. Obviously, this level of modification cannot ignore the influence of deformation. For this reason, this embodiment slices and calculates the deformation amount of the inner ring 1 of the bearing, and transfers the deformation amount to the modification equation of the tapered roller 2 when the raceway is non-linear, so as to reduce the influence of deformation on contact stress.

[0023] In order to calculate the deformation of the raceway, the method for determining the roller modification amount in the tapered roller bearing of this embodiment proposes a slicing method. In subsequent calculations, the slices are not related to each other, and the deformation at different positions can be calculated separately.

[0024] Specifically, the method of 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 includes: In the formula, x is the axial distance under the coordinate, y is s is the 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, is the semi-cone angle of the inner ring raceway.

[0025] like Figure 2 As shown in the figure, 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: In the formula, n is the number of roller track slices.

[0026] From this, the initial raceway radius of each slice can be obtained: At this point, the raceway is sliced ​​into n pieces. Each piece is calculated separately in the subsequent calculations without interfering with each other. The value of n is determined by the bearing size and the amount of calculation.

[0027] Considering the influence of temperature and interference on raceway deformation, calculate the raceway temperature rise deformation and the raceway radial expansion affected by interference for each slice. When calculating the influence of interference, since the interference during installation will change when the temperature rises, the interference after temperature rise should be used for calculation. The sum of the two gives the radial deformation of each slice.

[0028] In order to obtain a better contact stress distribution, it is necessary to make a difference in the deformation. Set the minimum value of the radial deformation to 0 (i.e. the reference point), and calculate the difference between the radial deformation of each slice and the minimum value of the radial deformation terminal: In the formula, y L is the difference between the radial deformation of each slice and the minimum value of the radial deformation, is the radial deformation of each slice, is the minimum value of the radial deformation of each slice.

[0029] To simplify the calculation, the roller modification amount is composed of the initial logarithmic modification amount and the deformation compensation. The initial logarithmic modification amount is calculated by the prior art based on the linear raceway.

[0030] In this embodiment, the initial logarithmic shaping amount includes the shaping amount corresponding to the Lundberg logarithmic equation or the Johns logarithmic equation. In other embodiments, other existing initial logarithmic shaping amounts may also be used. The specific initial logarithmic shaping amount belongs to the prior art and will not be repeated here.

[0031] Specifically, the initial logarithmic shaping amount is a method of calculating the linear raceway in the prior art, and the raceway is shaped using the Lundberg logarithmic equation or the Johns logarithmic equation. The difference between the radial deformation amount of each slice and the minimum value of the radial deformation amount is superimposed on the Lundberg logarithmic equation or the Johns logarithmic equation, as shown below: y = y d + y L In the formula, y is the modification amount of the roller in the tapered roller bearing, y d is the initial logarithmic shaping amount, y L is the difference between the radial deformation of each slice and the minimum value of the radial deformation. After analysis, it is found that if the radial deformation of each slice is directly used Correct the raceway and change the raceway radius of each slice of the raceway to ys Corrected to: y s — ); Recalculating the radial deformation of the raceway according to the corrected initial raceway radius equation of each slice will reveal that the radial deformation of each slice after calculation has not changed. Because the value of the raceway radius of each slice is much larger than the radial deformation of each slice, the radial deformation of each slice is swallowed up during the calculation process. Difference is made between the original deformation and the deformation calculated after the raceway correction, such as Figure 3 As shown, Figure 3 The ordinate is the difference, and the abscissa is the axial distance x under the coordinate. -9 level, almost 0. It can be seen that directly correcting the raceway cannot actually achieve the effect of correcting the deformation effect. 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 corresponding to the raceway to the modification amount of the roller, so as to make the roller surface shape more suitable for the actual state of the bearing during operation, thereby reducing the contact stress during contact.

[0032] Specifically, the difference between the radial deformation of each slice and the minimum value of the radial deformation is added to the initial logarithmic modification amount to obtain the modification amount of the roller in the tapered roller bearing.

[0033] In this embodiment, the method for 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 bearing working condition according to the thermal expansion coefficient of the bearing material, the raceway radius of each slice, normal temperature and the bearing working temperature.

[0034] Specifically, the temperature rise deformation of the raceway of each slice is as follows: In the formula, is the temperature rise deformation of the raceway of each slice, is the thermal expansion coefficient of the bearing ring material, y s is the raceway radius of each slice, T0 is the room temperature of 20℃, and T is the bearing operating temperature.

[0035] Among them, the thermal expansion coefficient of bearing steel is generally 12×10 -5 (1 / ℃).

[0036] In this embodiment, the method for determining the interference amount of the ring when the bearing is working includes: determining the interference amount of the ring when the bearing is working according to the thermal expansion coefficient of the bearing material, the thermal expansion coefficient of the mating part material, normal temperature, the bearing operating temperature and the interference amount set at normal temperature.

[0037] Specifically, the ring interference under the working condition of the bearing is as follows: In the formula, I FT is the interference of the ferrule after the raceway temperature rises, is the thermal expansion coefficient of the bearing ring material, 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 The interference set at room temperature. d represents a differential operator.

[0038] In this embodiment, the method of 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 ring under the working condition of the bearing and the raceway radius of each slice after temperature rise deformation.

[0039] Specifically, according to the interference of the ring under the working condition of the bearing and the raceway radius of each slice after temperature rise deformation, the radial expansion of the raceway caused by the interference of each slice is determined by the thick-walled ring theory equation as shown below: Where: 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 rises, y T is the raceway radius of each slice after temperature rise deformation, d is the bearing inner diameter, d m is the inner diameter of the shaft, is the Poisson's ratio of the bearing ring material, 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.

[0040] The inner diameter of a bearing d =150mm, shaft diameter 150mm, shaft hole d m =120mm, d i =193.465mm, L=54mm, =12°12'30''. Design interference I F 0.02mm. The initial temperature is 20℃ and the working temperature is 90℃. The thermal expansion coefficient of the bearing ring material 12.5×10 -6 (1 / ℃), elastic modulus E1=208000MPa, Poisson's ratio =0.3, thermal expansion coefficient of shaft material 11.7×10 -6(1 / ℃), elastic modulus E2=173000MPa, Poisson's ratio =0.3 as an example, the specific process example of the method for determining the roller modification amount in the tapered roller bearing of this embodiment is as follows: Step 1: Slice the bearing ring and calculate the raceway radius y of each slice according to the raceway shape equation s : In the formula, y s is the raceway radius of each slice.

[0041] Cut x into 54 parts at 1mm: .

[0042] The raceway radius of each slice can be obtained: .

[0043] Step 2: Calculate the temperature rise deformation of the raceway of each slice : In the formula, is the temperature rise deformation of the raceway of each slice, is the thermal expansion coefficient of the bearing ring material, y s is the raceway radius of each slice, T0 is the room temperature of 20℃, and T is the bearing operating temperature.

[0044] The temperature rise deformation of the raceway of each slice can be obtained : .

[0045] Step 3: Update the raceway radius of the ring slice y T = y s + : .

[0046] Step 4: Calculate the ring interference at the bearing operating temperature I FT : In the formula, I FT is the interference of the ferrule after the raceway temperature rises, is the thermal expansion coefficient of the bearing ring material, is the thermal expansion coefficient of the shaft material, T0 is the room temperature of 20°C, T is the bearing operating temperature, I FThe interference set at room temperature. d represents a differential operator.

[0047] Step 5: Calculate the radial expansion of the raceway caused by the interference of each slice under working conditions : Where: 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 rises, y T is the raceway radius of each slice after temperature rise deformation, d is the bearing inner diameter, d m is the inner diameter of the shaft, is the Poisson's ratio of the bearing ring material, 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; .

[0048] Step 6: Calculate the radial deformation of each slice : .

[0049] Step 7: Set the minimum value of the radial deformation to 0, and calculate the difference between the radial deformation of each slice and the minimum value of the radial deformation: In the formula, y L is the difference between the radial deformation of each slice and the minimum value of the radial deformation, is the radial deformation of each slice, is the minimum value of the radial deformation of each slice; .

[0050] Step 8: Output the roller modification amount y in the tapered roller bearing: y = y d + y L In the formula, y d is the initial logarithmic shaping amount; .

[0051] The roller surface is convexly modified according to the final modification amount.

[0052] Depend on Figure 4 The original shaping curve and the shaping curve obtained in this embodiment are compared, where the ordinate is the shaping amount y , the horizontal axis is the axial distance x under the coordinate; after considering more factors, the modified curve obtained in this embodiment has a modified value that is obviously different from the original modified curve and is more consistent with the actual situation of the deformed raceway.

[0053] Specific implementation methods are given above, but the present invention is not limited to the described implementation methods. The basic idea of ​​the present invention lies in the above basic scheme. For ordinary technicians in this field, it does not take creative work to design various deformed models, formulas, and parameters according to the teachings of the present invention. Changes, modifications, substitutions, and variations of the implementation methods without departing from the principles and spirit of the present invention still fall within the scope of protection 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 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; determining the raceway radial expansion of each slice using the raceway radius of each slice determined on the basis of the initial raceway radius and the interference of the ring under the working condition of the bearing; adding the difference between the radial deformation of each slice including the raceway radial expansion and the minimum value of the radial deformation including the raceway radial expansion to the initial logarithmic modification amount, and obtaining the modification amount of the roller in the tapered roller bearing.

2. The method for determining the roller modification amount in a tapered roller bearing according to claim 1, characterized in that: The radial deformation also includes the raceway temperature rise deformation; 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 raceway radius of each slice determined on the basis of the initial raceway radius is determined by updating the raceway radius of each slice based on the raceway temperature rise deformation.

3. 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: In the formula, x is the axial distance under the coordinate, y is s is the 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, is the semi-cone angle of the inner ring raceway.

4. The method for determining the roller modification amount in a tapered roller bearing according to claim 2 or 3, 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 raceway radius of each slice, the normal temperature and the bearing working temperature.

5. The method for determining the roller modification amount in a tapered roller bearing according to claim 1 or 2, 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.

6. The method for determining the roller modification amount in a tapered roller bearing according to claim 2, characterized in that: The method of 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 ring under the working condition of the bearing and the raceway radius of each slice after temperature rise deformation.

7. The method for determining the roller modification amount in a tapered roller bearing according to claim 4, characterized in that: The temperature rise deformation of the raceway of each slice is as follows: In the formula, is the temperature rise deformation of the raceway of each slice, is the thermal expansion coefficient of the bearing ring material, y s is the raceway radius of each slice, T0 is the room temperature of 20℃, and T is the bearing operating temperature.

8. The method for determining roller modification amount in a tapered roller bearing according to claim 5, characterized in that: The interference of the rings under the working condition of the bearing is as follows: In the formula, I FT is the interference of the ferrule after the raceway temperature rises, is the thermal expansion coefficient of the bearing ring material, 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 The interference set at room temperature. d is the differential operator.

9. The method for determining the roller modification amount in a tapered roller bearing according to claim 6, characterized in that: According to the interference of the ring under the working condition of the bearing and the raceway radius of each slice after temperature rise deformation, the radial expansion of the raceway caused by the interference of each slice is determined by the thick-walled ring theory equation as shown below: Where: 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 rises, y T is the raceway radius of each slice after temperature rise deformation, d is the bearing inner diameter, d m is the inner diameter of the shaft, is the Poisson's ratio of the bearing ring material, 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.

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