A main differential lubrication structure

Abstract

The utility model discloses a main differential lubrication structure, including main reducer casing, be provided with first oil storage cavity on the inner chamber of main reducer casing, and the both sides of first oil storage cavity are equipped with the order oil inlet and reverse oil inlet, and the bottom of order oil inlet and reverse oil inlet is opened to the oil groove, and the oil groove is set to the axial center line direction of interaxial differential mechanism to guide the flow direction of lubricating oil interaxial differential mechanism's meshing area. The utility model discloses through setting first oil storage cavity on main reducer casing, and setting the oil groove to the gear of interaxial differential mechanism at its bottom, and the centrifugal force of interaxial differential mechanism gear rotation is used to introduce lubricating oil from order / reverse oil inlet to oil storage cavity, and then lubricating oil is accurately dropped to the gear meshing area through oil groove, realizes directional self -lubricating.

Description

Technical Field

[0001] This utility model relates to the field of differential lubrication technology, specifically to a lubrication structure for a main differential. Background Technology

[0002] As a core component of the drive axle, the lubrication performance of the main reducer directly affects the reliability and service life of the transmission system. In a through-drive axle structure, the lubrication of the inter-shaft differential is particularly critical. Currently, the industry commonly uses splash lubrication for both the main reducer and the inter-shaft differential. This method utilizes a high-speed rotating oil pan, gears, and other components to atomize the lubricating oil in the oil sump into droplets or mist, covering the parts requiring lubrication, eliminating the need for a pressure oil supply system such as an oil pump. Under normal operating conditions, splash lubrication allows the rotating gears to spray lubricating oil, meeting the lubrication requirements of the inter-shaft differential.

[0003] However, under special operating conditions such as heavy-load uphill driving, the lubricating oil level in the main reducer housing drops due to the vehicle's inclination, leading to uneven oil distribution. Furthermore, under low-speed, high-torque conditions, the main reducer's input speed is lower, reducing the gears' ability to agitate the oil and significantly decreasing oil splash. This can easily result in insufficient lubrication of the inter-axle differential, accelerating wear on gears and bearings and severely impacting the differential's service life.

[0004] Furthermore, existing technologies typically employ methods such as increasing the amount of lubricating oil and raising the oil level to improve the lubrication effect of the inter-shaft differential. However, in practical applications, this method offers limited improvement in lubrication, especially under extreme operating conditions where sufficient lubrication cannot be guaranteed. On the other hand, excessive lubricating oil can increase the resistance to oil churning in the gears, resulting in a significant increase in overall energy loss, reduced transmission efficiency, and hindering energy conservation and emission reduction. Utility Model Content

[0005] To solve the above-mentioned technical problems, this utility model specifically provides the following technical solution:

[0006] A main differential lubrication structure includes a main reducer housing, wherein the top of the inner cavity of the main reducer housing protrudes downward to form a first oil reservoir.

[0007] The forward oil inlet and the reverse oil inlet are both located on the side wall of the first oil reservoir along the rotational tangent direction of the inter-shaft differential gear.

[0008] The forward oil inlet is configured to collect centrifugally separated lubricating oil when the inter-shaft differential gear rotates clockwise;

[0009] The reverse oil inlet is configured to collect centrifugally separated lubricating oil when the inter-shaft differential gear rotates counterclockwise;

[0010] An oil groove is provided at the bottom of both the forward oil inlet and the reverse oil inlet, and is positioned toward the axial centerline of the inter-shaft differential to guide the lubricating oil to the meshing area of ​​the inter-shaft differential.

[0011] As a preferred embodiment of this utility model, the first oil reservoir has a tapered inverted trapezoidal structure in cross section along the axis of the inter-shaft differential main shaft to guide the lubricating oil into the oil sump.

[0012] As a preferred embodiment of the present invention, a main differential lubrication structure further includes an oil guiding structure. The oil guiding structure includes a second oil storage chamber. The second oil storage chamber is disposed on the main reducer housing and arranged adjacent to the first oil storage chamber. The second oil storage chamber is simultaneously provided with the forward oil inlet and the reverse oil inlet.

[0013] The main reducer housing cover is fixedly connected to the main reducer housing. A lubrication channel is formed inside the main reducer housing cover. The oil outlet of the second oil reservoir is sealed to the oil inlet of the lubrication channel. The oil outlet of the lubrication channel is set towards the bearing on the side of the inter-shaft differential.

[0014] The oil guiding structure collects the lubricating oil that is centrifugally separated when the inter-shaft differential gear rotates through the second oil storage chamber, and directs the lubricating oil to the rotating area of ​​the bearing through the lubrication channel.

[0015] As a preferred embodiment of this utility model, the main reducer housing cover is generally in the shape of a frustum cone. The large diameter end of the main reducer housing cover is fixedly connected to the main reducer housing. The oil inlet end of the lubrication channel is located on the large diameter end of the main reducer housing cover. The oil inlet end and the oil outlet end of the lubrication channel are arranged on the conical peripheral wall of the main reducer housing cover with a height difference.

[0016] As a preferred embodiment of this utility model, an annular lubrication channel is provided on the inner wall of the main reducer housing cover, the bearing is fitted into the annular lubrication channel, and the oil outlet end of the lubrication channel is connected to the annular lubrication channel.

[0017] As a preferred embodiment of the present invention, an arc-shaped oil baffle is integrally formed on the inner wall of the main reducer housing cover. The arc-shaped oil baffle extends along the arc-shaped inner wall of the main reducer housing cover and protrudes radially from the inner circumferential wall of the main reducer housing cover. The arc-shaped oil baffle is axially opposite to the end face of the inter-shaft differential gear.

[0018] The arc-shaped oil baffle is configured to prevent axial lubricating oil splashing generated when the inter-shaft differential gear rotates.

[0019] As a preferred embodiment of this utility model, the inner edge of the radial bottom end of the arc-shaped oil baffle is formed with a guide surface, and the guide surface is arranged toward the thrust shim between the gear and the bearing of the inter-shaft differential.

[0020] Compared with the prior art, this utility model has the following advantages:

[0021] This invention features a first oil reservoir on the main reducer housing, with an oil groove at its bottom facing the inter-shaft differential gear. The centrifugal force of the rotating gear draws lubricating oil into the reservoir from the forward / reverse inlet. The oil then drips precisely into the gear meshing area through the groove, achieving directional self-lubrication. This effectively overcomes the lubrication insufficiency caused by oil level drops and speed reductions in traditional splash lubrication under heavy loads and uphill conditions. It ensures a stable oil supply to the inter-shaft differential even at low speeds and high torque, significantly improving lubrication reliability. Simultaneously, it avoids energy loss from excessive oil agitation, balancing lubrication effectiveness and transmission efficiency, extending differential lifespan, and reducing overall machine energy consumption. Attached Figure Description

[0022] To more clearly illustrate the embodiments of this utility model or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings in the following description are merely exemplary, and those skilled in the art can derive other embodiments based on the provided drawings without creative effort.

[0023] Figure 1 This is an exploded view of the components of this utility model;

[0024] Figure 2 This is an assembly drawing of the present invention;

[0025] Figure 3 This is a partial cross-sectional assembly drawing of the present invention;

[0026] Figure 4 This is a top sectional view of the main reducer housing of this utility model;

[0027] Figure 5 This utility model Figure 4 Enlarged view of point A in the middle;

[0028] Figure 6 This is a side sectional view of the main reducer housing of this utility model;

[0029] Figure 7 This utility model Figure 6 Enlarged view of point B in the middle;

[0030] Figure 8This is a cross-sectional view of the main reducer housing cover of this utility model.

[0031] The labels in the diagram represent the following:

[0032] 1. Main reducer housing; 2. First oil reservoir; 3. Forward oil inlet; 4. Reverse oil inlet; 5. Inter-shaft differential gear; 6. Oil groove; 7. Inter-shaft differential; 8. Second oil reservoir; 9. Main reducer housing cover; 10. Lubrication channel; 11. Bearing; 12. Annular lubrication channel; 13. Arc-shaped oil baffle; 14. Guide surface; 15. Thrust pad. Detailed Implementation

[0033] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.

[0034] like Figures 1 to 8 As shown, this utility model provides a main differential lubrication structure, including a main reducer housing 1, a forward oil inlet 3, a reverse oil inlet 4, and an oil groove 6. The main reducer housing 1 is a metal casting, with its inner cavity top protruding downwards to form a first oil reservoir 2, used to collect lubricating oil centrifugally separated when the inter-shaft differential gear 5 rotates. The cross-sectional shape of the first oil reservoir 2 is designed to effectively collect lubricating oil. The forward oil inlet 3 and the reverse oil inlet 4 are respectively opened on the side wall of the first oil reservoir 2 along the rotational tangent direction of the inter-shaft differential gear 5. Specifically, the forward oil inlet 3 is located on one side of the first oil reservoir 2, and its opening direction is consistent with the tangent direction when the inter-shaft differential gear 5 rotates clockwise, thereby effectively collecting the lubricating oil thrown out by centrifugal force when the gear rotates clockwise. Similarly, the reverse oil inlet 4 is located on the other side of the first oil reservoir 2, and its opening direction is consistent with the tangent direction when the inter-shaft differential gear 5 rotates counterclockwise, used to collect the lubricating oil thrown out during counterclockwise rotation. Specifically, an annular groove can be opened on the main reducer housing 1, and the inter-shaft differential gear 5 can be fitted and rotated in the annular groove. At the same time, the first oil storage chamber 2 is set in the annular groove, so that the forward oil inlet 3 and the reverse oil inlet 4 of the first oil storage chamber 2 can be set along the tangential direction of the inter-shaft differential gear 5, thereby enabling stable oil intake.

[0035] like Figure 5As shown, the dimensions and shapes of the forward oil inlet 3 and the reverse oil inlet 4 are optimized according to the gear speed and lubricating oil flow requirements. For example, rectangular or arc-shaped openings are used, with arc-shaped oil guide surfaces at the openings to maximize oil collection efficiency. An oil groove 6 is formed through the bottom of both the forward and reverse oil inlets 3 and extends towards the axial centerline of the inter-shaft differential 7. The oil groove 6 has a groove-like structure with a U-shaped or rectangular cross-section; its depth and width are determined according to the actual flow requirements of the lubricating oil. The design of the oil groove 6 ensures that the collected lubricating oil can flow smoothly to the meshing area of ​​the inter-shaft differential 7, thereby providing sufficient lubrication for the gear meshing parts and reducing friction and wear.

[0036] The first oil reservoir 2 has a cross-section designed as a tapering inverted trapezoidal structure along the axis of the main shaft of the inter-shaft differential 7. Specifically, the top of the first oil reservoir 2 is wider and the bottom is narrower, forming an inverted trapezoidal space that gradually narrows along the axial direction. This design allows the lubricating oil to slide more easily along the inner wall of the inverted trapezoid to the bottom under centrifugal force and eventually flow into the oil sump 6. The inclination angle of the inverted trapezoidal structure can be adjusted according to the operating speed of the differential and the viscosity of the lubricating oil.

[0037] like Figure 3 As shown, the main differential lubrication structure further includes an oil guiding structure, which is used to directionally deliver lubricating oil to the rotating area of ​​the bearing 11. The oil guiding structure includes a second oil reservoir 8 and a main reducer housing cover 9. The second oil reservoir 8 is disposed on the main reducer housing 1 and is arranged adjacent to the first oil reservoir 2. The structure of the second oil reservoir 8 is similar to that of the first oil reservoir 2, with the top also protruding downwards for collecting lubricating oil. The second oil reservoir 8 is simultaneously provided with a forward oil inlet 3 and a reverse oil inlet 4, the position and function of which are the same as those of the forward oil inlet 3 and the reverse oil inlet 4 of the first oil reservoir 2, for collecting lubricating oil when the inter-shaft differential gear 5 rotates clockwise or counterclockwise. The main reducer housing cover 9 is fixedly connected to the main reducer housing 1 by flange bolts, and a lubrication flow channel 10 is formed inside it. The lubrication flow channel 10 is a channel that runs through the main reducer housing cover 9, and its oil inlet end forms a sealed connection with the oil outlet of the second oil reservoir 8. The oil outlet of the lubrication channel 10 is positioned facing the bearing 11 on the side of the inter-shaft differential 7, allowing the lubricating oil to flow directly to the rotating area of ​​the bearing 11, providing lubrication and cooling for the bearing 11. The cross-sectional shape of the lubrication channel 10 can be circular or rectangular, and its diameter or width is designed according to the lubricating oil flow requirements.

[0038] like Figure 3As shown, the main reducer housing 9 has an overall frustoconical structure, with its large-diameter end fixedly connected to the main reducer housing 1. The oil inlet of the lubrication channel 10 is located on the large-diameter end of the main reducer housing 9, while the oil outlet is located on the conical peripheral wall or small-diameter end of the main reducer housing 9, aligned with the bearing 11. There is a height difference between the oil inlet and the oil outlet. Specifically, the oil inlet is located at a higher position, and the oil outlet is located at a lower position. This height difference design utilizes gravity to assist the flow of lubricating oil, improving the conveying efficiency.

[0039] like Figure 8 As shown, an annular lubrication channel 12 is formed on the inner wall of the main reducer housing 9. The annular lubrication channel 12 is an annular groove extending circumferentially along the inner wall of the main reducer housing 9, and its depth and width are designed according to the size of the bearing 11 and the lubrication requirements. The bearing 11 is fitted into the annular lubrication channel 12 to ensure a tight fit between the bearing 11 and the annular lubrication channel 12. The oil outlet end of the lubrication channel 10 is connected to the annular lubrication channel 12, so that the lubricating oil can be evenly distributed in the rotating area of ​​the bearing 11, reducing the friction and temperature rise of the bearing 11.

[0040] like Figure 3 As shown, an arc-shaped oil baffle 13 is integrally formed on the inner wall of the main reducer housing 9. The arc-shaped oil baffle 13 extends along the arc-shaped inner wall of the main reducer housing 9 and protrudes radially from the inner circumferential wall of the main reducer housing 9. The arc-shaped oil baffle 13 is axially opposite to the end face of the inter-shaft differential gear 5, and is used to prevent axial lubricating oil splashing generated when the gear rotates. Since the inter-shaft differential gear 5 is a cylindrical helical gear, when the cylindrical helical gear rotates, the lubricating oil moves in both the tangential direction and the axial direction under the action of centrifugal force. The design of the arc-shaped oil baffle 13 can block the separation of lubricating oil in the axial direction. The curvature of the arc-shaped oil baffle 13 matches the curvature of the inner wall of the main reducer housing 9. The length of the arc-shaped oil baffle can be a section as shown in the figure, which is positioned to block the upper edge of the inter-shaft differential gear 5.

[0041] The inner edge of the radial bottom end of the arc-shaped oil baffle 13 forms a guide surface 14. The guide surface 14 is a smooth arc or inclined structure, facing the thrust washer 15 between the inter-shaft differential gear 5 and the bearing 11. The guide surface 14 allows the lubricating oil intercepted by the arc-shaped oil baffle 13 to flow along the guide surface 14 to the area of ​​the thrust washer 15, thereby providing lubrication for the thrust washer 15 and reducing its wear and friction. The thrust washer 15 is made of wear-resistant high-strength steel, which can prevent direct axial contact between the inter-shaft differential gear 5 and the input shaft, and delay the wear of both when the speeds of the inter-shaft differential gear 5 and the input shaft are different.

[0042] The above embodiments are merely exemplary embodiments of this application and are not intended to limit this application. The scope of protection of this application is defined by the claims. Those skilled in the art can make various modifications or equivalent substitutions to this application within its substance and scope of protection, and such modifications or equivalent substitutions should also be considered to fall within the scope of protection of this application.

Claims

1. A lubrication structure for a main differential, characterized in that, include: The main reducer housing (1) has a first oil reservoir (2) formed by the downward protrusion of the top of the inner cavity of the main reducer housing (1). Forward oil inlet (3) and reverse oil inlet (4) are both opened on the side wall of the first oil reservoir (2) along the rotational tangent direction of the inter-shaft differential gear (5); The forward oil inlet (3) is configured to collect centrifugally separated lubricating oil when the inter-shaft differential gear (5) rotates clockwise; The reverse oil inlet (4) is configured to collect centrifugally separated lubricating oil when the inter-shaft differential gear (5) rotates counterclockwise; Oil groove (6) is provided at the bottom of the forward oil inlet (3) and the reverse oil inlet (4). The oil groove (6) is arranged in the direction of the axial center line of the inter-shaft differential (7) to guide the lubricating oil to the meshing area of ​​the inter-shaft differential (7).

2. The main differential lubrication structure according to claim 1, characterized in that: The first oil reservoir (2) has a tapered inverted trapezoidal structure in the cross section along the axis of the main shaft of the inter-shaft differential (7) to guide the lubricating oil into the oil trough (6).

3. The main differential lubrication structure according to claim 1 or 2, characterized in that, It also includes an oil guiding structure, the oil guiding structure comprising: The second oil storage chamber (8) is disposed on the main reducer housing (1) and arranged adjacent to the first oil storage chamber (2). The forward oil inlet (3) and the reverse oil inlet (4) are simultaneously opened on the second oil storage chamber (8). The main reducer housing cover (9) is fixedly connected to the main reducer housing (1). A lubrication channel (10) is formed inside the main reducer housing cover (9). The oil outlet of the second oil reservoir (8) is sealed to the oil inlet of the lubrication channel (10). The oil outlet of the lubrication channel (10) is set towards the bearing (11) on the side of the inter-shaft differential (7). The oil guiding structure collects the lubricating oil separated by centrifugal force when the inter-shaft differential gear (5) rotates through the second oil storage chamber (8), and directs the lubricating oil to the rotation area of ​​the bearing (11) via the lubrication channel (10).

4. The main differential lubrication structure according to claim 3, characterized in that, The main reducer housing cover (9) is generally in the shape of a frustum cone. The large diameter end of the main reducer housing cover (9) is fixedly connected to the main reducer housing (1). The oil inlet end of the lubrication channel (10) is located on the large diameter end of the main reducer housing cover (9). The oil inlet end and the oil outlet end of the lubrication channel (10) are set on the conical peripheral wall of the main reducer housing cover (9) with a height difference.

5. The main differential lubrication structure according to claim 3, characterized in that, The inner wall of the main reducer housing cover (9) is provided with an annular lubrication channel (12), the bearing (11) is fitted into the annular lubrication channel (12), and the oil outlet end of the lubrication channel (10) is connected to the annular lubrication channel (12).

6. The main differential lubrication structure according to claim 4 or 5, characterized in that, An arc-shaped oil baffle (13) is integrally formed on the inner wall of the main reducer housing cover (9). The arc-shaped oil baffle (13) extends along the arc-shaped inner wall of the main reducer housing cover (9) and protrudes radially from the inner circumferential wall of the main reducer housing cover (9). The arc-shaped oil baffle (13) is axially opposite to the end face of the inter-shaft differential gear (5). The arc-shaped oil baffle (13) is configured to prevent axial lubricating oil splashing generated when the inter-shaft differential gear (5) rotates.

7. The main differential lubrication structure according to claim 6, characterized in that, The inner edge of the radial bottom end of the arc-shaped oil baffle (13) is formed with a guide surface (14), which is set toward the thrust pad (15) between the inter-shaft differential gear (5) and the bearing (11).

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