A main reduction gear assembly structure

Abstract

The application relates to a main reducer assembly structure which comprises a main reducer shell assembly, an inter-axle differential assembly, an input flange assembly, a bearing seat assembly, a bevel gear pair assembly and an output shaft assembly; the bevel gear pair assembly and the input flange are respectively connected with the inter-axle differential assembly through spline connection, the inter-axle differential assembly is rotationally connected with the output shaft assembly; the cam type inter-axle differential is adopted to replace the planetary gear type inter-axle differential, and the cylindrical gear pair transmission is cancelled, so that the structure is simple, the assembly efficiency is high, the whole bridge weight can be reduced, the cam type inter-axle differential has higher friction torque and higher torque ratio, and the reliability of the inter-axle differential can be improved.

Description

Technical Field

[0001] This invention relates to the field of automotive parts technology, and in particular to a main reducer assembly structure. Background Technology

[0002] In existing three-axle vehicles, the intermediate axle (also known as the through axle) is connected to the gearbox via a driveshaft. The gearbox is connected to the engine, which transmits power to the through axle. The through axle then distributes power to the left and right wheels and the rear drive axle. When the vehicle is turning or traversing uneven surfaces, to prevent tire slippage and premature tire wear, an inter-axle differential is required to allow the intermediate and rear axle tires to maintain different rotational speeds. Current inter-axle differentials are mostly planetary gear differentials, which consist of half-shaft gears, planetary gears, left and right differential housings, and gaskets. Additionally, the input shaft and drive bevel gear of the current through axle are connected by a pair of cylindrical gears with a 1:1 ratio.

[0003] The shortcomings of the existing solution are: 1. The planetary gear differential has a complex structure, requires adjustment of tooth backlash during assembly, has low assembly efficiency, and has a high failure rate for after-sales components such as half-shaft gears and shims; 2. Adding a pair of cylindrical gears to the transmission results in a complex structure and greater weight for the main reducer assembly. Summary of the Invention

[0004] The purpose of this invention is to address the shortcomings of existing technologies by providing a new main reducer assembly structure. This structure replaces the planetary gear type with a cam-type inter-shaft differential and eliminates the cylindrical gear pair transmission, resulting in a simpler structure, higher assembly efficiency, and overall axle weight reduction. Furthermore, the cam-type inter-shaft differential has higher frictional torque and a higher torque ratio, improving the reliability of the inter-shaft differential.

[0005] This invention is achieved using the following technical solution:

[0006] A main reducer assembly structure includes a main reducer housing assembly, an inter-shaft differential assembly, an input flange assembly, a bevel gear pair assembly, and an output shaft assembly;

[0007] The inter-shaft differential assembly is housed within the input flange assembly, and the bevel gear assembly and output shaft assembly are respectively housed within the main reducer housing assembly. The input flange and bevel gear assembly are splinedly connected to the inter-shaft differential assembly, and the inter-shaft differential assembly is through-fitted with the output shaft assembly.

[0008] Preferably, the inter-shaft differential includes an input shaft, an outer differential housing, and several sliders;

[0009] The input shaft includes a column with a spline structure, a bearing positioning boss, and a first hollow cylinder;

[0010] The cylinder is connected to the input flange spline, and the first hollow cylinder is provided with two rings of several holes, with a phase difference between the two rings of holes.

[0011] Preferably, the outer differential housing includes a second hollow cylinder with a spline structure and a third hollow cylinder that is stepped with the second hollow cylinder;

[0012] The inner side of the third hollow cylinder is provided with several protrusions, and a groove is formed between two adjacent protrusions.

[0013] Preferably, the slider is a cylindrical structure with arc surfaces at both ends.

[0014] Preferably, the output shaft assembly includes an output shaft, one end of which is provided with two rows of several protrusions, and a groove is formed between two adjacent protrusions in the same row, and the two rows of protrusions have a phase difference.

[0015] The second protrusion and the second groove are respectively provided with a first end of a slider, and the second end of the slider passes through a matching hole and is connected to the first protrusion and the first groove respectively.

[0016] Preferably, the bevel gear assembly includes a drive bevel gear, which has a hollow structure, and the second hollow cylinder is connected to the inner wall of the drive bevel gear by a spline.

[0017] Preferably, it also includes a bearing housing assembly, which includes a bearing one, a bearing two, a cup-shaped preload sleeve, and a twelve-corner nut connected to the drive bevel gear.

[0018] Preferably, the third hollow cylinder is provided with a plurality of oil passage holes evenly distributed on it.

[0019] Compared with the prior art, the present invention has the following beneficial technical effects:

[0020] 1. This invention uses a cam-type inter-shaft differential instead of a planetary gear differential, which has a simple structure, eliminates the need to adjust gear backlash, and significantly increases assembly efficiency; the cam-type inter-shaft differential has higher friction torque and higher torque ratio, which can improve the reliability of the inter-shaft differential.

[0021] 2. Compared with the planetary gear differential, the distance between the input flange end face and the center of the axle is greatly shortened in the cam-type inter-shaft differential of this invention;

[0022] 3. This invention eliminates the cylindrical gear pair transmission, and the weight of the main reducer assembly is lighter than that of the existing structure. Attached Figure Description

[0023] The invention will be further described below with reference to the accompanying drawings:

[0024] Figure 1This is a front view of the overall structure of the present invention;

[0025] Figure 2 This is a top view of the overall structure of the present invention;

[0026] Figure 3 This is a schematic diagram of the external differential housing structure of the present invention;

[0027] Figure 4 This is a schematic diagram of the input shaft structure of the present invention;

[0028] Figure 5 This is a schematic diagram of the slider structure of the present invention;

[0029] Figure 6 This is a schematic diagram of the output shaft structure of the present invention.

[0030] Explanation of reference numerals in the attached figures

[0031] 1-Main reducer housing assembly, 2-Inter-shaft differential assembly, 3-Input flange assembly, 4-Bearing housing assembly, 5-Bevel gear assembly, 6-Output shaft assembly, 21-Input shaft, 22-Outer differential housing, 23-Slider, 41-Dodecagonal nut, 42-Bearing one, 43-Cup-shaped preload sleeve, 44-Bearing two, 51-Drive bevel gear, 61-Output shaft, 211-Cylinder, 212-Bearing positioning boss, 213-Hole, 214-First hollow cylinder, 221-Second hollow cylinder, 222-Third hollow cylinder, 223-Protrusion one, 224-Groove two, 225-Oil passage hole, 231-Arc surface, 611-Groove two, 612-Protrusion two. Detailed Implementation

[0032] To better understand the above-mentioned objectives, features, and advantages of the present invention, the present invention will be described in detail below with reference to the accompanying drawings and specific embodiments. It should be noted that, unless otherwise explicitly specified and limited, the embodiments and features described in the embodiments of this application can be combined with each other. In the description of the present invention, it should also be noted that, unless otherwise explicitly specified and limited, the terms "set," "install," and "connect" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal communication between two components. Those skilled in the art can understand the specific meaning of the above terms in the present invention based on the specific circumstances.

[0033] Example 1:

[0034] like Figure 1-6As shown: A main reducer assembly structure includes a main reducer housing assembly 1, an inter-shaft differential assembly 2, an input flange assembly 3, a bearing housing assembly 4, a bevel gear pair assembly 5, and an output shaft assembly 6; the weight of this main reducer assembly is 12% to 15% lighter than that of existing structures;

[0035] like Figure 2 As shown, the inter-axle differential assembly 2 includes an input shaft 21, an outer differential housing 22, and several sliders 23, forming a cam-type inter-axle differential. Replacing the planetary gear differential with a cam-type differential simplifies the structure, eliminates the need to adjust gear backlash, and improves assembly efficiency by approximately 10%. The cam-type differential has higher friction torque and a higher torque ratio, which improves the reliability of the inter-axle differential. Compared to the planetary gear differential, the distance from the input flange end face to the axle center can be reduced by approximately 10%.

[0036] like Figure 3 As shown, the input shaft 21 includes a column 211 splined to the input flange 3, a bearing positioning boss 212, and a first hollow cylinder 214. The first hollow cylinder 214 has two rings of evenly distributed holes 213. The two rings of holes have a 15° phase difference, that is, the holes in one row correspond to the middle of two holes in the other row. The holes are the same size and there are 12 holes in a single row.

[0037] like Figure 4 As shown, the outer differential housing 22 includes a second hollow cylinder 221 and a third hollow cylinder 222. The inner side of the third hollow cylinder 222 is composed of 6 sets of protrusions 223 and grooves 224. The number of protrusions 223 and grooves 224 are equal and 6 in total. Six oil passage holes 225 are evenly arranged on the third hollow cylinder 222. The outer side of the second hollow cylinder 221 has a spline structure.

[0038] like Figure 6 As shown, the end of the output shaft 61 consists of two rows, each row having 6 sets of protrusions 612 and grooves 611. The two rows of protrusions 612 and grooves 611 have a 30° phase difference. One row of protrusions 612 and the other row of grooves 611 are opposite each other. The number of protrusions 612 and grooves 611 is equal and is 6.

[0039] like Figure 5 As shown, the slider 23 has a cylindrical structure with arc surfaces 231 at both ends. The arc surfaces 231 cooperate with the protrusion 223 and groove 224 of the outer differential housing 22 and the input shaft 21, and the protrusion 612 and groove 611 of the output shaft 61.

[0040] like Figure 1 As shown, the driving bevel gear 51 in the bevel gear assembly 5 has a hollow structure, and the second hollow cylinder 221 is splinedly connected to the driving bevel gear 51.

[0041] like Figure 1 As shown, the bearing housing assembly 4 includes a first bearing 42, a second bearing 44, a cup-shaped preload sleeve 43, and a dodecagonal nut 41 for connecting to the drive bevel gear 51; the bearing preload force is adjusted by the cup-shaped preload sleeve 43.

[0042] The working principle is as follows: Power is input from the engine to the input flange assembly 2 of the through axle through the gearbox. The input flange assembly 2 is connected to the input shaft 21 through a spline, which transmits power to the input shaft 21. The input shaft 21 drives the slider 23 to rotate. The slider 23 cooperates with the protrusions 223, 612 and grooves 224, 611 on the outer differential housing 22 and the output shaft 61, which drive the outer differential housing 22 and the output shaft 61 to rotate together. The outer differential housing 22 is connected to the driving bevel gear 51 through a spline, which drives the driving bevel gear 51 to rotate. The driving bevel gear 51 drives the driven bevel gear to rotate through the meshing of the driven bevel gear. Then, through the inter-wheel differential half-shaft gear, the power is transmitted to the two wheels. The output shaft 61 is connected to the rear drive axle input flange assembly through the drive shaft, which transmits power to the rear drive axle.

[0043] It will be apparent to those skilled in the art that the present invention is not limited to the details of the exemplary embodiments described above, and that the invention can be implemented in other specific forms without departing from its spirit or essential characteristics. Therefore, the embodiments should be considered in all respects as exemplary and non-limiting, and the scope of the invention is defined by the appended claims rather than the foregoing description. Thus, all variations falling within the meaning and scope of the equivalent elements of the claims are intended to be included within the present invention. No reference numerals in the claims should be construed as limiting the scope of the claims.

[0044] The above-described embodiments are only used to illustrate the technical solutions of the present invention, and are not intended to limit it. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A main reducer assembly structure, characterized by, The main reducer shell assembly (1), the interaxle differential assembly (2), the input flange assembly (3), the bevel gear pair assembly (5), the output shaft assembly (6); The interaxle differential assembly (2) is arranged in the input flange assembly (3), the bevel gear pair assembly (5) and the output shaft assembly (6) are arranged in the main reducer shell assembly (1) respectively, the input flange assembly (3) and the bevel gear pair assembly (5) are connected with the interaxle differential assembly (2) by spline respectively, the interaxle differential assembly (2) is connected with the output shaft assembly (6) by through cooperation. The interaxle differential assembly (2) comprises an input shaft (21), an outer differential shell (22) and a plurality of sliding blocks (23). The input shaft (21) comprises a column (211) with a spline structure, a bearing positioning boss (212) and a first hollow cylinder (214). The column (211) is connected with the input flange assembly (3) by spline, a plurality of holes (213) are arranged on the first hollow cylinder (214), and the two circles of holes (213) have a phase difference. The outer differential shell (22) comprises a second hollow cylinder (221) with a spline structure and a third hollow cylinder (222) arranged in steps with the second hollow cylinder (221). A plurality of protrusions one (223) are arranged on the inner side of the third hollow cylinder (222), and a groove one (224) is formed between the adjacent two protrusions one (223). The output shaft assembly (6) comprises an output shaft (61), and the output shaft (61) is provided with two rows of a plurality of protrusions two (612) at one end, a groove two (611) is formed between the adjacent two protrusions two (612) in the same row, and the two rows of protrusions two (612) have a phase difference. The sliding block (23) is arranged on the first end of the protrusions two (612) and the groove two (611) respectively, and the second end of the sliding block (23) penetrates through the matched hole (213) and is connected with the protrusion one (223) and the groove one (224) by through cooperation.

2. The main reduction gear assembly structure of claim 1, wherein The sliding block (23) is a cylindrical structure with a circular arc surface (231) at both ends.

3. The main reducer assembly structure of claim 1, wherein, The bevel gear pair assembly (5) comprises a driving bevel gear (51), the driving bevel gear (51) is a hollow structure, and the second hollow cylinder (221) is connected with the inner wall of the driving bevel gear (51) by spline.

4. The main reduction gear assembly structure of claim 3, wherein The bearing seat assembly (4) comprises a bearing one (42) connected with the driving bevel gear (51), a bearing two (44), a cup-shaped pre-tightening sleeve (43) and a twelve-corner nut (41).

5. The main reduction gear assembly structure of claim 1, wherein A plurality of oil channel holes (225) are uniformly arranged on the third hollow cylinder (222).

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