A method for matching the interface size of a drive shaft and a reducer

Abstract

The present application relates to a method for matching the interface size of a drive shaft and a reducer, and belongs to the technical field of automobile drive shafts. The method includes setting the initial value of the outer diameter of the matching section between the movable joint and the inner hole support surface of the differential housing; calculating the total eccentricity of the movable joint at the main lip of the oil seal and the imbalance of the drive shaft; judging whether the calculated total eccentricity is within the preset eccentricity range, and judging whether the calculated imbalance is within the preset imbalance range, if not, increasing the initial value of the outer diameter and returning to the previous step, if so, the initial value of the outer diameter meets the requirements. The total eccentricity of the movable joint at the main lip of the oil seal and the imbalance of the drive shaft can be calculated to determine whether the interface matching size is reasonable. If it is unreasonable, the initial value of the outer diameter of the matching section between the movable joint and the inner hole support surface of the differential housing can be adjusted to lock the interface design size, so as to avoid the vibration problem of the reducer oil seal and the whole vehicle in the subsequent actual vehicle testing stage, thereby reducing manpower and development costs.

Description

Technical Field

[0001] The present application relates to the technical field of automobile drive shafts, and in particular to a method for matching the interface dimensions of a drive shaft and a reducer. Background Art

[0002] The power output port of the automobile transmission is assembled with the drive shaft, and an oil seal is installed at the transmission output port to prevent the lubricating oil in the transmission from leaking out. Therefore, a dustproof structure needs to be designed to protect the oil seal from damage.

[0003] In the related art, the Chinese patent with patent number CN206503913U proposes a dustproof structure at the interface between the drive shaft and the transmission, the dustproof structure includes a transmission, a drive shaft interface provided on the transmission, a detachable transmission oil seal provided on the drive shaft interface, a drive shaft connected to the transmission through the transmission oil seal and the drive shaft interface, and a detachable dust cover provided on the drive shaft, the transmission oil seal includes an oil seal body, a first oil seal dust cover provided on the outside of the oil seal body to prevent dust, a second oil seal dust cover provided at one end of the oil seal body to prevent dust, and an oil seal lip provided on the inside of the oil seal body. The technical problem of the risk of external sand and dust entering the transmission output port, damaging the oil seal lip, and then causing oil leakage at the transmission output port is solved.

[0004] However, the above structure does not consider the effect of the matching between the reducer differential housing and the drive shaft handle on oil seal leakage and vehicle vibration. If the matching size design is unreasonable, the eccentricity of the drive shaft handle at the oil seal will be too large, which will lead to increased wear of the oil seal and subsequent oil leakage, which will also cause vehicle vibration. Therefore, it is necessary to propose a method for matching the drive shaft and reducer interface dimensions to avoid oil seal leakage and vehicle vibration problems caused by unreasonable matching design of the drive shaft and reducer interface in the early stage, and reduce manpower and development costs. Summary of the invention

[0005] The embodiment of the present application provides a method for matching the dimensions of a drive shaft and a reducer interface, so as to solve the problems of oil seal leakage and vehicle vibration caused by unreasonable matching design of the interface between the automobile drive shaft and the reducer in the related art.

[0006] The embodiment of the present application provides a method for matching the dimensions of a drive shaft and a reducer interface, comprising the following steps:

[0007] Design the diameter and support length of the inner hole of the differential housing on the reducer assembled with the drive shaft, the weight of the moving joint and the shaft on the drive shaft, the distance from the design center of the moving joint to the support surface of the inner hole of the differential housing, and the distance from the main lip of the oil seal on the reducer to the support surface of the inner hole of the differential housing;

[0008] Set the initial value of the outer diameter of the matching section between the moving joint and the inner hole support surface of the differential shell;

[0009] Calculate the total eccentricity of the moving joint at the main lip of the oil seal and the unbalance of the drive shaft;

[0010] Determine whether the calculated total eccentricity is within the preset eccentricity range, and determine whether the calculated unbalance is within the preset unbalance range. If not, increase the initial value of the outer diameter and return to the previous step. If so, the initial value of the outer diameter meets the requirements.

[0011] In some embodiments, calculating the total eccentricity of the moving joint at the main lip of the oil seal specifically includes:

[0012] When the moving joint is inscribed in the supporting surface of the inner hole of the differential housing and the central axis of the moving joint and the inner hole of the differential housing are parallel to each other, the static eccentricity of the moving joint at the main lip of the oil seal is calculated according to the diameter of the inner hole of the differential housing and the initial value of the outer diameter of the matching section between the moving joint and the supporting surface of the inner hole of the differential housing;

[0013] When the moving joint is tilted to the limit position in the inner hole of the differential housing, the single-side eccentric angle of the moving joint at the main lip of the oil seal is calculated according to the diameter and support length of the inner hole of the differential housing and the initial value of the outer diameter of the matching section between the moving joint and the support surface of the inner hole of the differential housing;

[0014] Calculate the unilateral eccentricity of the movable joint at the main lip of the oil seal according to the unilateral eccentricity angle of the movable joint at the main lip of the oil seal and the distance from the main lip of the oil seal to the supporting surface of the inner hole of the differential housing;

[0015] The total eccentricity of the movable joint at the main lip of the oil seal is calculated based on the static eccentricity and unilateral eccentricity of the movable joint at the main lip of the oil seal.

[0016] In some embodiments, calculating the unilateral eccentric angle of the moving joint at the main lip of the oil seal specifically includes:

[0017] According to the diameter of the inner hole of the differential shell and the support length, a first angle formed by the diagonal line of the inner hole of the differential shell and the end face of the inner hole of the differential shell is calculated;

[0018] According to the diameter of the inner hole of the differential housing and the support length, and the initial value of the outer diameter of the matching section between the moving joint and the supporting surface of the inner hole of the differential housing, the second angle formed by the diagonal line of the inner hole of the differential housing and the transverse section of the moving joint is calculated;

[0019] The single-sided eccentric angle of the moving joint at the main lip of the oil seal is calculated based on the first angle formed by the diagonal line of the inner hole of the differential housing and the end face of the inner hole of the differential housing and the second angle formed by the diagonal line of the inner hole of the differential housing and the transverse section of the moving joint.

[0020] In some embodiments, calculating the imbalance of the drive shaft specifically includes:

[0021] According to the unilateral eccentricity angle of the movable joint at the main lip of the oil seal, calculate the unilateral eccentricity of the movable joint at the design center;

[0022] Calculate the center of gravity offset radius of the drive shaft based on the unilateral eccentricity of the drive shaft at the design center of the movable joint and the static eccentricity of the movable joint at the main lip of the oil seal;

[0023] Calculate the unbalanced mass of the drive shaft based on the mass of the moving joint and the mass of the shaft;

[0024] The unbalance amount of the drive shaft is calculated based on the unbalanced mass of the drive shaft and the offset radius of the center of gravity of the drive shaft.

[0025] In some embodiments, the total eccentricity E of the moving joint at the main lip of the oil seal is calculated as follows:

[0026] E=2×(S1+S2)

[0027] Among them, S1 is the static eccentricity of the movable joint at the main lip of the oil seal, and S2 is the unilateral eccentricity of the movable joint at the main lip of the oil seal.

[0028] In some embodiments, the static eccentricity S1 of the moving joint at the main lip of the oil seal is calculated as follows:

[0029]

[0030] The calculation method of the first angle θ1 is:

[0031] θ1=tan -1 (L1÷D1)

[0032] The calculation method of the second angle θ2 is:

[0033] θ2=cos -1 {d2÷(L1÷sinθ1)}

[0034] The calculation method of the single-sided eccentric angle α of the moving joint at the main lip of the oil seal is:

[0035] α=θ2-θ1

[0036] The calculation method of the unilateral eccentricity S2 of the moving joint at the main lip of the oil seal is:

[0037] S2=tanα×L2

[0038] Among them, L1 is the support length of the inner hole of the differential housing, D1 is the diameter of the inner hole of the differential housing, d2 is the initial value of the outer diameter of the matching section between the moving node and the support surface of the inner hole of the differential housing, and L2 is the distance from the main lip of the oil seal to the support surface of the inner hole of the differential housing.

[0039] In some embodiments, the calculation method of the unbalance i of the drive shaft is:

[0040] i=m×r

[0041] Where m is the unbalanced mass of the drive shaft, and r is the offset radius of the center of gravity of the drive shaft.

[0042] In some embodiments, the unbalanced mass m of the drive shaft is calculated as follows:

[0043]

[0044] The calculation method of the unilateral eccentricity S3 of the drive shaft at the design center of the movable joint is:

[0045] S3=tanα×L3

[0046] The calculation method of the center of gravity offset radius r of the drive shaft is:

[0047] r=S1+S3

[0048] Among them, m1 is the mass of the shaft, m2 is the mass of the moving joint, α is the unilateral eccentricity angle of the moving joint at the main lip of the oil seal, L3 is the distance from the design center of the moving joint to the support surface of the inner hole of the differential housing, and S1 is the static eccentricity of the moving joint at the main lip of the oil seal.

[0049] In some embodiments, the preset eccentricity range is 0 to 0.4 mm, and the preset unbalance range is 0 to 1500 gmm.

[0050] In some embodiments, the determining whether the calculated total eccentricity is within a preset eccentricity range and determining whether the calculated unbalance is within a preset unbalance range further includes:

[0051] If not, increase the support length of the inner hole of the differential shell and return to the previous step.

[0052] The beneficial effects of the technical solution provided by this application include:

[0053] The embodiment of the present application provides a method for matching the dimensions of a drive shaft and a reducer interface, and the method comprises the following steps:

[0054] Design the diameter and support length of the inner hole of the differential housing on the reducer assembled with the drive shaft, the weight of the moving joint and the shaft on the drive shaft, the distance from the design center of the moving joint to the support surface of the inner hole of the differential housing, and the distance from the main lip of the oil seal on the reducer to the support surface of the inner hole of the differential housing;

[0055] Set the initial value of the outer diameter of the matching section between the moving joint and the inner hole support surface of the differential shell;

[0056] Calculate the total eccentricity of the moving joint at the main lip of the oil seal and the unbalance of the drive shaft;

[0057] Determine whether the calculated total eccentricity is within the preset eccentricity range, and determine whether the calculated unbalance is within the preset unbalance range. If not, increase the initial value of the outer diameter and return to the previous step. If so, the initial value of the outer diameter meets the requirements.

[0058] Therefore, by building a matching model of the drive shaft handle and the reducer differential housing, the total eccentricity of the movable joint at the main lip of the oil seal and the imbalance of the drive shaft can be calculated to determine whether the interface matching size is reasonable. If it is unreasonable, the initial value of the outer diameter of the matching section between the movable joint and the inner hole support surface of the differential housing can be adjusted to lock the interface design size, so as to avoid the reducer oil seal and vehicle jitter problems in the subsequent actual vehicle testing stage, thereby reducing manpower and development costs. BRIEF DESCRIPTION OF THE DRAWINGS

[0059] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings required for use in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without creative work.

[0060] Figure 1 This is a schematic diagram of the structure of an embodiment of the present application;

[0061] Figure 2 This is a simplified model diagram of an embodiment of the present application.

[0062] In the accompanying drawings, the components represented by the reference numerals are listed as follows:

[0063] 100, driving shaft; 101, shaft; 102, moving joint; 200, reducer; 201, main lip of oil seal; 202, inner hole of differential housing. DETAILED DESCRIPTION

[0064] In order to make the purpose, technical solution and advantages of the embodiments of the present application clearer, the technical solution in the embodiments of the present application will be clearly and completely described below in conjunction with the drawings in the embodiments of the present application. Obviously, the described embodiments are part of the embodiments of the present application, not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without making creative work are within the scope of protection of this application.

[0065] The embodiment of the present application provides a method for matching the dimensions of a drive shaft and a reducer interface, which can solve the problems of oil seal leakage and vehicle vibration caused by unreasonable matching design of the automobile drive shaft and reducer interface in the related art.

[0066] See also Figure 1 and Figure 2As shown, the embodiment of the present application provides a method for matching the size of a drive shaft and a reducer interface, comprising the following steps:

[0067] 1) Design the diameter and support length of the differential housing inner hole 202 on the reducer 200 assembled with the drive shaft 100, the weight of the moving joint 102 and the shaft 101 on the drive shaft 100, the distance from the design center of the moving joint 102 to the support surface of the differential housing inner hole 202, and the distance from the main lip 201 of the oil seal on the reducer 200 to the support surface of the differential housing inner hole 202;

[0068] 2) Setting the initial value of the outer diameter of the matching section between the moving joint 102 and the supporting surface of the differential housing inner hole 202;

[0069] 3) Calculate the total eccentricity of the movable joint 102 at the oil seal main lip 201 and the unbalance of the drive shaft 100;

[0070] 4) Determine whether the calculated total eccentricity is within the preset eccentricity range, and determine whether the calculated unbalance is within the preset unbalance range. If not, increase the initial value of the outer diameter and return to the previous step. If so, the initial value of the outer diameter meets the requirements.

[0071] The data in steps 1 and 2 of the embodiment of the present application can refer to the manufacturing data of relevant automobile parts, and then the total eccentricity of the movable joint 102 at the oil seal main lip 201 and the unbalance of the drive shaft 100 are calculated to quantify the total eccentricity of the movable joint 102 at the oil seal main lip 201 and the unbalance of the drive shaft 100 after the interface matching, so as to quantitatively judge whether the interface matching is reasonable. If it is unreasonable, the initial value of the outer diameter of the matching section between the movable joint 102 and the supporting surface of the differential shell inner hole 202 can be adjusted to lock the interface design size, so as to avoid oil seal leakage and vehicle vibration problems caused by unreasonable interface matching design of the drive shaft 100 and the reducer 200 in the early stage, thereby reducing manpower and development costs.

[0072] It should be noted that the support length of the inner hole 202 of the differential housing is the length that can effectively support the moving joint 102, and does not include the depth of the chamfer opened at the end of the inner hole 202 of the differential housing for auxiliary installation;

[0073] The design center of the movable joint 102 is the existing technology. The movable joint 102 on the drive shaft 100 has a design center. The inner joint on the shaft 101 is installed at the design center inside the movable joint 102 to meet the slippage of ±25mm.

[0074] When the interface size is not properly matched, the initial value of the outer diameter increases by 0.01 to 0.1 mm each time.

[0075] In some alternative embodiments: See Figure 1 and Figure 2As shown, the embodiment of the present application provides a method for matching the interface size of a drive shaft and a reducer. The method for matching the interface size of a drive shaft and a reducer mentioned in the calculation of the total eccentricity of the moving joint 102 at the main lip 201 of the oil seal specifically includes:

[0076] When the support surface of the moving joint 102 and the differential housing inner hole 202 are inscribed and the central axes of the moving joint 102 and the differential housing inner hole 202 are parallel to each other, the static eccentricity of the moving joint 102 at the oil seal main lip 201 is calculated according to the diameter of the differential housing inner hole 202 and the initial value of the outer diameter of the matching section between the moving joint 102 and the support surface of the differential housing inner hole 202;

[0077] When the moving joint 102 is tilted to the extreme position in the differential housing inner hole 202, the single-side eccentric angle of the moving joint 102 at the oil seal main lip 201 is calculated according to the diameter and support length of the differential housing inner hole 202 and the initial value of the outer diameter of the matching section between the moving joint 102 and the support surface of the differential housing inner hole 202;

[0078] Calculate the unilateral eccentricity of the movable joint 102 at the oil seal main lip 201 according to the unilateral eccentricity angle of the movable joint 102 at the oil seal main lip 201 and the distance from the oil seal main lip 201 to the supporting surface of the differential housing inner hole 202;

[0079] The total eccentricity of the movable joint 102 at the oil seal main lip 201 is calculated according to the static eccentricity and the unilateral eccentricity of the movable joint 102 at the oil seal main lip 201 .

[0080] The static eccentricity and unilateral eccentricity of the embodiment of the present application can be measured by constructing a simplified model schematic diagram using the data of steps 1 and 2. The static eccentricity is the distance from the center axis of the moving joint 102 to the center axis of the inner hole 202 of the differential shell when the support surface of the moving joint 102 and the inner hole 202 of the differential shell are inscribed and the center axes of the moving joint 102 and the inner hole 202 of the differential shell are parallel to each other.

[0081] In some alternative embodiments: See Figure 1 and Figure 2 As shown, the embodiment of the present application provides a method for matching the interface size of a drive shaft and a reducer. The method for matching the interface size of a drive shaft and a reducer mentioned in the calculation of the unilateral eccentric angle of the moving joint 102 at the main lip 201 of the oil seal specifically includes:

[0082] Calculate a first angle formed by a diagonal line of the differential housing inner hole 202 and an end face of the differential housing inner hole 202 according to the diameter of the differential housing inner hole 202 and the support length;

[0083] According to the diameter and support length of the differential housing inner hole 202 and the initial value of the outer diameter of the matching section between the moving joint 102 and the supporting surface of the differential housing inner hole 202, the second angle formed by the diagonal line of the differential housing inner hole 202 and the transverse section of the moving joint 102 is calculated;

[0084] The unilateral eccentric angle of the moving joint 102 at the oil seal main lip 201 is calculated based on the first angle formed by the diagonal line of the differential housing inner hole 202 and the end face of the differential housing inner hole 202 and the second angle formed by the diagonal line of the differential housing inner hole 202 and the transverse section of the moving joint 102.

[0085] The unilateral eccentric angle of the movable joint 102 at the oil seal main lip 201 of the embodiment of the present application is the angle formed by the central axis of the movable joint 102 and the central axis of the differential housing inner hole 202 when the movable joint 102 is tilted to the extreme position in the differential housing inner hole 202.

[0086] In some alternative embodiments: See Figure 1 and Figure 2 As shown, an embodiment of the present application provides a method for matching the interface size of a drive shaft and a reducer. The method for matching the interface size of a drive shaft and a reducer mentions the calculation of the unbalance amount of the drive shaft 100, which specifically includes:

[0087] According to the unilateral eccentricity angle of the movable joint 102 at the oil seal main lip 201, the unilateral eccentricity of the movable joint 102 at the design center is calculated;

[0088] The center of gravity offset radius of the drive shaft 100 is calculated according to the unilateral eccentricity of the drive shaft 100 at the design center of the moving joint 102 and the static eccentricity of the moving joint 102 at the main lip 201 of the oil seal;

[0089] Calculate the unbalanced mass of the drive shaft 100 according to the mass of the moving joint 102 and the mass of the shaft 101;

[0090] The unbalance amount of the drive shaft 100 is calculated based on the unbalanced mass of the drive shaft 100 and the radius of the center of gravity offset of the drive shaft 100 .

[0091] The unbalance amount of the drive shaft 100 in the embodiment of the present application is equal to the unbalance mass of the drive shaft 100 multiplied by the gravity center offset radius of the drive shaft 100 .

[0092] It should be noted that the unbalanced mass of the drive shaft 100 is the mass of the drive shaft 100 at the design center of the movable joint 102. Since the center of gravity formed by the inner section on the shaft 101 of the drive shaft 100 will shift during the rotation of the movable joint 102, the distance that the center of gravity deviates from the central axis of the inner hole 202 of the differential housing is the center of gravity offset radius of the drive shaft 100. The center of gravity offset radius of the drive shaft 100 is equal to the unbalanced mass of the drive shaft 100 plus the center of gravity offset radius of the drive shaft 100.

[0093] In some alternative embodiments: See Figure 1 and Figure 2As shown, the embodiment of the present application provides a method for matching the interface size of a drive shaft and a reducer. The method for calculating the total eccentricity E of the movable joint 102 at the main lip 201 of the oil seal mentioned in the method for matching the interface size of the drive shaft and the reducer is:

[0094] E=2×(S1+S2)

[0095] Wherein, S1 is the static eccentricity of the movable joint 102 at the oil seal main lip 201 , and S2 is the unilateral eccentricity of the movable joint 102 at the oil seal main lip 201 .

[0096] The total eccentricity of the movable joint 102 at the oil seal main lip 201 of the embodiment of the present application can be understood as the degree of extrusion on the oil seal main lip 201. The larger the total eccentricity, the greater the degree of extrusion deformation of the oil seal main lip 201, and the easier it is for the oil seal main lip 201 to leak oil. Therefore, the total eccentricity must be within a preset reasonable range to ensure that there will be no oil seal leakage problem.

[0097] In some alternative embodiments: See Figure 1 and Figure 2 As shown, the embodiment of the present application provides a method for matching the interface size of a drive shaft and a reducer. The method for matching the interface size of a drive shaft and a reducer mentioned in the method for matching the interface size of the drive shaft and the reducer is used to calculate the static eccentricity S1 of the moving joint 102 at the main lip 201 of the oil seal as follows:

[0098]

[0099] The calculation method of the first angle θ1 is:

[0100] θ1=tan -1 (L1÷D1)

[0101] The calculation method of the second angle θ2 is:

[0102] θ2=cos -1 {d2÷(L1÷sinθ1)}

[0103] The calculation method of the unilateral eccentric angle α of the moving joint 102 at the oil seal main lip 201 is:

[0104] α=θ2-θ1

[0105] The calculation method of the unilateral eccentricity S2 of the moving joint 102 at the oil seal main lip 201 is:

[0106] S2=tanα×L2

[0107] Among them, L1 is the support length of the differential housing inner hole 202, D1 is the diameter of the differential housing inner hole 202, d2 is the initial value of the outer diameter of the matching section between the moving joint 102 and the support surface of the differential housing inner hole 202, and L2 is the distance from the oil seal main lip 201 to the support surface of the differential housing inner hole 202.

[0108] The embodiment of the present application can quantitatively calculate the static eccentricity S1 of the movable joint 102 at the oil seal main lip 201 and the unilateral eccentricity S2 of the movable joint 102 at the oil seal main lip 201 by building a simplified model of the driving shaft 100 and the reducer 200.

[0109] It should be noted that see Figure 2 As shown, the rectangle with a diameter of d2 corresponds to the moving joint 102, and the rectangle with a diameter of L1 corresponds to the inner hole 202 of the differential shell. When the moving joint 102 and the supporting surface of the inner hole 202 of the differential shell are inscribed and the central axis of the moving joint 102 and the inner hole 202 of the differential shell are parallel to each other, the single side of the rectangle with a diameter of d2 and the single side of the rectangle with a diameter of L1 coincide.

[0110] By drawing an auxiliary line OA on a rectangle with a diameter of d2, when the movable joint 102 is tilted to the limit position in the inner hole 202 of the differential housing, OA coincides with OA', and the position of the movable joint 102 after tilting corresponds to Figure 2 The position of the middle dotted line can be used to calculate the first angle θ1 formed by the diagonal line OA' of the differential shell inner hole 202 and the end face of the differential shell inner hole 202, and the second angle θ2 formed by the diagonal line OA' of the differential shell inner hole 202 and the transverse section of the movable joint 102 (the section of the movable joint 102 perpendicular to its central axis at the inclined position), and the second angle θ2 is also equal to the angle formed by the auxiliary line OA and the end face of the differential shell inner hole 202.

[0111] In some alternative embodiments: See Figure 1 and Figure 2 As shown, the embodiment of the present application provides a method for matching the interface size of a drive shaft and a reducer. The method for calculating the unbalance amount i of the drive shaft 100 mentioned in the method for matching the interface size of the drive shaft and the reducer is:

[0112] i=m×r

[0113] Wherein, m is the unbalanced mass of the drive shaft 100 , and r is the radius of the center of gravity offset of the drive shaft 100 .

[0114] In some alternative embodiments: See Figure 1 and Figure 2 As shown, the embodiment of the present application provides a method for matching the interface size of a drive shaft and a reducer. The method for calculating the unbalanced mass m of the drive shaft 100 mentioned in the method for matching the interface size of the drive shaft and the reducer is:

[0115]

[0116] The calculation method of the unilateral eccentricity S3 of the drive shaft 100 at the design center of the moving joint 102 is:

[0117] S3=tanα×L3

[0118] The calculation method of the center of gravity offset radius r of the drive shaft 100 is:

[0119] r=S1+S3

[0120] Among them, m1 is the mass of the shaft 101, m2 is the mass of the movable joint 102, α is the unilateral eccentricity angle of the movable joint 102 at the oil seal main lip 201, L3 is the distance from the design center of the movable joint 102 to the supporting surface of the differential housing inner hole 202, and S1 is the static eccentricity of the movable joint 102 at the oil seal main lip 201.

[0121] The shaft 101 of the drive shaft 100 of the embodiment of the present application is connected and supported at both ends during use, and each end connection support shares half of the weight. Therefore, when calculating the unbalanced mass of the drive shaft 100, half of the mass of the shaft 101 and the mass of the movable joint 102 are added.

[0122] The present application proposes a method for matching the interface dimensions of a drive shaft and a reducer, and can create a model calculation table to quantify the eccentricity of the shank of the drive shaft 100 at the oil seal and the imbalance of the drive shaft 100 after the interface matching, so as to quantitatively judge whether the interface matching is reasonable, so as to avoid oil seal leakage and vehicle vibration problems caused by unreasonable interface matching design of the drive shaft 100 and the reducer 200 in the early stage, thereby reducing manpower and development costs.

[0123] It should be noted that the support length L1 of the differential housing inner hole 202, the distance L2 from the oil seal main lip 201 to the support surface of the differential housing inner hole 202, the distance L3 from the design center of the movable joint 102 to the support surface of the differential housing inner hole 202, and the diameter D1 of the differential housing inner hole 202 all include manufacturing tolerances when determining, among which L2, L3, and D1 can take the maximum dimensional values ​​under their respective tolerance requirements, and L1 can take the minimum dimensional value under the tolerance requirements. If the calculated total deviation and imbalance meet the requirements, it can be guaranteed that the interface dimensions under the condition of taking the tolerance boundary value for processing also meet the matching design requirements.

[0124] Exemplarily, the model calculation table is as follows:

[0125]

[0126] In some alternative embodiments: See Figure 1 and Figure 2As shown, an embodiment of the present application provides a method for matching the dimensions of a drive shaft and a reducer interface. The method for matching the dimensions of a drive shaft and a reducer interface mentions a preset eccentricity range of 0 to 0.4 mm and a preset unbalance range of 0 to 1500 g / mm.

[0127] The embodiment of the present application controls the range of the eccentricity and the unbalance, thereby facilitating quantitative judgment of whether the calculated total eccentricity E and the unbalance i meet the requirements, and further facilitating determination of whether the interface matching dimensions are reasonable.

[0128] In some alternative embodiments: See Figure 1 and Figure 2 As shown, an embodiment of the present application provides a method for matching the size of a drive shaft and a reducer interface. The method for matching the size of a drive shaft and a reducer interface includes judging whether the calculated total eccentricity is within a preset eccentricity range and judging whether the calculated unbalance is within a preset unbalance range. The method also includes:

[0129] If not, increase the support length of the differential housing inner hole 202 and return to the previous step.

[0130] The embodiment of the present application can meet the requirements of total eccentricity and unbalance by increasing the support length of the differential housing inner hole 202. For example, when the requirements cannot be met by adjusting the initial value d2 of the outer diameter of the matching section between the moving joint 102 and the support surface of the differential housing inner hole 202, the support length L of the differential housing inner hole 202 can be corrected until the total eccentricity and unbalance meet the requirements.

[0131] It should be noted that the other design data of the support length L of the inner hole 202 of the differential shell in step 1 can also be modified to meet the requirements of the total eccentricity and unbalance.

[0132] In the description of the present application, it should be noted that the terms "upper", "lower", etc. 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 application 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 cannot be understood as a limitation on the present application. Unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be an indirect connection through an intermediate medium, or it can be a connection between the two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present application can be understood according to the specific circumstances.

[0133] It should be noted that, in this application, relational terms such as "first" and "second" are only used to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Moreover, the terms "include", "comprise" or any other variants thereof are intended to cover non-exclusive inclusion, so that a process, method, article or device including a series of elements includes not only those elements, but also other elements not explicitly listed, or also includes elements inherent to such process, method, article or device. In the absence of further restrictions, the elements defined by the sentence "comprise a ..." do not exclude the presence of other identical elements in the process, method, article or device including the elements.

[0134] The above description is only a specific implementation of the present application, so that those skilled in the art can understand or implement the present application. Various modifications to these embodiments will be apparent to those skilled in the art, and the general principles defined herein can be implemented in other embodiments without departing from the spirit or scope of the present application. Therefore, the present application will not be limited to the embodiments shown herein, but will conform to the widest range consistent with the principles and novel features applied for herein.

Claims

1. A method for matching the interface size of a drive shaft and a reducer, characterized in that: The following steps are involved: Design the diameter and support length of the inner hole (202) of the differential housing on the reducer (200) assembled with the drive shaft (100), the weight of the moving joint (102) and the shaft (101) on the drive shaft (100), the distance from the design center of the moving joint (102) to the support surface of the inner hole (202) of the differential housing, and the distance from the main lip (201) of the oil seal on the reducer (200) to the support surface of the inner hole (202) of the differential housing; Setting an initial value of the outer diameter of the matching section between the moving joint (102) and the supporting surface of the differential housing inner hole (202); Calculating the total eccentricity of the moving joint (102) at the oil seal main lip (201) and the unbalance of the drive shaft (100); Determine whether the calculated total eccentricity is within the preset eccentricity range, and determine whether the calculated unbalance is within the preset unbalance range. If not, increase the initial value of the outer diameter and return to the previous step. If so, the initial value of the outer diameter meets the requirements.

2. The method for matching the drive shaft and reducer interface dimensions according to claim 1, characterized in that: Calculating the total eccentricity of the moving joint (102) at the oil seal main lip (201) specifically includes: When the support surface of the moving joint (102) and the differential housing inner hole (202) are inscribed and the central axes of the moving joint (102) and the differential housing inner hole (202) are parallel to each other, the static eccentricity of the moving joint (102) at the oil seal main lip (201) is calculated according to the diameter of the differential housing inner hole (202) and the initial value of the outer diameter of the matching section between the moving joint (102) and the support surface of the differential housing inner hole (202); When the moving joint (102) is tilted to an extreme position in the differential housing inner hole (202), the single-side eccentric angle of the moving joint (102) at the oil seal main lip (201) is calculated according to the diameter and support length of the differential housing inner hole (202) and the initial value of the outer diameter of the matching section between the moving joint (102) and the support surface of the differential housing inner hole (202); Calculating the unilateral eccentricity of the moving joint (102) at the oil seal main lip (201) according to the unilateral eccentricity angle of the moving joint (102) at the oil seal main lip (201) and the distance from the oil seal main lip (201) to the supporting surface of the differential housing inner hole (202); The total eccentricity of the moving joint (102) at the oil seal main lip (201) is calculated based on the static eccentricity and the unilateral eccentricity of the moving joint (102) at the oil seal main lip (201).

3. The method for matching the drive shaft and reducer interface dimensions as claimed in claim 2, characterized in that: Calculating the unilateral eccentric angle of the moving joint (102) at the oil seal main lip (201) specifically includes: Calculating a first angle formed by a diagonal line of the differential shell inner hole (202) and an end face of the differential shell inner hole (202) according to the diameter of the differential shell inner hole (202) and the support length; Calculating a second angle formed by a diagonal line of the differential housing inner hole (202) and a transverse cross section of the movable joint (102) based on the diameter and support length of the differential housing inner hole (202) and the initial value of the outer diameter of the matching section between the movable joint (102) and the support surface of the differential housing inner hole (202); The single-sided eccentric angle of the moving joint (102) at the oil seal main lip (201) is calculated based on a first angle formed by a diagonal line of the differential housing inner hole (202) and an end face of the differential housing inner hole (202) and a second angle formed by a diagonal line of the differential housing inner hole (202) and a transverse cross section of the moving joint (102).

4. The method for matching the drive shaft and reducer interface dimensions as claimed in claim 3, characterized in that: Calculating the unbalance of the drive shaft (100) specifically includes: Calculating the unilateral eccentricity of the movable joint (102) at the design center according to the unilateral eccentricity angle of the movable joint (102) at the oil seal main lip (201); Calculating the center of gravity offset radius of the drive shaft (100) based on the unilateral eccentricity of the drive shaft (100) at the design center of the moving joint (102) and the static eccentricity of the moving joint (102) at the main lip (201) of the oil seal; Calculating the unbalanced mass of the drive shaft (100) according to the mass of the moving joint (102) and the mass of the shaft (101); The unbalance amount of the drive shaft (100) is calculated based on the unbalanced mass of the drive shaft (100) and the gravity center offset radius of the drive shaft (100).

5. The method for matching the drive shaft and reducer interface dimensions as claimed in claim 4, characterized in that: The calculation method of the total eccentricity E of the moving joint (102) at the oil seal main lip (201) is: E=2×(S1+S2) Wherein, S1 is the static eccentricity of the movable joint (102) at the oil seal main lip (201), and S2 is the unilateral eccentricity of the movable joint (102) at the oil seal main lip (201).

6. The method for matching the drive shaft and reducer interface dimensions as claimed in claim 5, characterized in that: The calculation method of the static eccentricity S1 of the moving joint (102) at the oil seal main lip (201) is: The calculation method of the first angle θ1 is: θ1=tan -1 (L1÷D1) The calculation method of the second angle θ2 is: θ2=cos -1 {d2÷(L1÷sinθ1)} The calculation method of the single-side eccentric angle α of the moving joint (102) at the oil seal main lip (201) is: α=θ2-θ1 The calculation method of the unilateral eccentricity S2 of the moving joint (102) at the oil seal main lip (201) is: S2=tanα×L2 Wherein, L1 is the support length of the differential housing inner hole (202), D1 is the diameter of the differential housing inner hole (202), d2 is the initial value of the outer diameter of the matching section between the moving joint (102) and the support surface of the differential housing inner hole (202), and L2 is the distance from the main lip of the oil seal (201) to the support surface of the differential housing inner hole (202).

7. The method for matching the drive shaft and reducer interface dimensions as claimed in claim 6, characterized in that: The calculation method of the unbalance i of the drive shaft (100) is: i=m×r Wherein, m is the unbalanced mass of the drive shaft (100), and r is the radius of the center of gravity offset of the drive shaft (100).

8. The method for matching the drive shaft and reducer interface dimensions as claimed in claim 7, characterized in that: The unbalanced mass m of the drive shaft (100) is calculated as follows: The calculation method of the unilateral eccentricity S3 of the drive shaft (100) at the design center of the moving joint (102) is: S3=tanα×L3 The calculation method of the center of gravity offset radius r of the drive shaft (100) is: r=S1+S3 Wherein, m1 is the mass of the shaft (101), m2 is the mass of the movable joint (102), α is the single-sided eccentricity angle of the movable joint (102) at the main lip (201) of the oil seal, L3 is the distance from the design center of the movable joint (102) to the supporting surface of the inner hole (202) of the differential housing, and S1 is the static eccentricity of the movable joint (102) at the main lip (201) of the oil seal.

9. The method for matching the drive shaft and reducer interface dimensions as claimed in claim 1, characterized in that: The preset eccentricity range is 0 to 0.4 mm, and the preset unbalance range is 0 to 1500 gmm.

10. The method for matching the interface size of a drive shaft and a reducer according to claim 1, characterized in that: The step of judging whether the calculated total eccentricity is within a preset eccentricity range and judging whether the calculated unbalance is within a preset unbalance range further comprises: If not, increase the support length of the differential housing inner hole (202) and return to the previous step.

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