A main drive assembly for a drive axle of a construction machine

Abstract

The present application relates to the technical fields of engineering machinery transmission, and specifically relates to an engineering machinery drive axle main transmission assembly, which comprises a differential case, a driving spiral bevel gear and a large spiral bevel gear that are engaged with each other, the large spiral bevel gear is connected with the differential case, the driving spiral bevel gear transmits force to the large spiral bevel gear, the large spiral bevel gear changes the transmission direction of the force and drives the wheel to rotate, the driving spiral bevel gear is provided with a main spiral bearing and an oil seal, the main spiral bearing and the oil seal are assembled on a main transmission shell, the main transmission shell is provided with an oil groove group for lubricating the main spiral bearing and the oil seal, flexible spacer sleeves are arranged between the inner rings of the main spiral bearing, and a differential assembly with a locking function is arranged in the differential case. The present application can improve the whole machine passability in complex road conditions, optimize the process in the assembly process of the assembly, and reduce the assembly cost and the part cost.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of engineering machinery transmission, and specifically provides an engineering machinery drive axle main transmission assembly. BACKGROUND

[0002] Engineering machinery is an important part of the equipment industry, mainly used in national defense construction engineering, transportation construction, energy industry construction, raw material industry construction such as production mine, agricultural and water conservancy construction, industrial and civil building city construction, environmental protection and other fields. The drive axle assembly is an important part of the engineering machinery, mainly used for power transmission and load bearing, the drive axle assembly transmits the power provided by the engine to the wheel edge of the vehicle, thereby driving the vehicle to move forward or backward, at the same time, the drive axle assembly also bears the function of bearing the weight of the vehicle and steering, the drive axle assembly plays a vital role in the engineering machinery, and the performance thereof directly affects the operation efficiency and safety of the engineering machinery.

[0003] The drive axle main transmission, as an important part of the drive axle assembly, is mainly composed of helical gear pairs, differential assemblies and other components, and the main role thereof in the drive axle assembly is to increase torque and change the direction of force transmission. The traditional engineering machinery drive axle main transmission has the following disadvantages:

[0004] 1. The lubrication effect of the bearing position of the driving bolt is poor, and the lubrication design is unreasonable, which will result in that the bearing and oil seal cannot be sufficiently lubricated and cooled in the harsh high-speed running environment; it can also result in that the oil flows back to the housing in the uphill and downhill working conditions of the whole machine, and cannot be stored in the bearing and oil seal, so that the bearing and oil seal cannot be sufficiently lubricated and cooled in the working condition, and damage occurs.

[0005] 2. The differential of the traditional differential does not have the characteristics of differential force, which results in that the structure of the differential is not suitable for the ground working condition with large difference in ground adhesion.

[0006] 3. The driving helical gear of part of the differential is a cantilever structure under stress, which needs to meet the requirements of bearing clearance control while having sufficient bolt tightening force, and it is more complex to adjust the bearing clearance by using a gasket.

[0007] 4. The gasket of the planetary gear is mostly made of copper material, which will greatly increase the cost.

[0008] In summary, how to design an engineering machinery drive axle main transmission assembly with good lubrication effect, which can ensure the passability of the whole machine under various road conditions, can solve the complex problem of adjusting bearing clearance, and can reduce the cost, is an urgent problem to be solved at present. SUMMARY

[0009] The application provides an engineering machinery drive axle main transmission assembly, which can solve the problems of poor lubrication, poor machine passability when the ground adhesion force difference is large, bearing play complexity and high cost.

[0010] The application provides an engineering machinery drive axle main transmission assembly, which comprises a differential case, a driving spiral bevel gear and a large spiral bevel gear that are in engagement with each other, the large spiral bevel gear is connected with the differential case, the driving spiral bevel gear transmits force to the large spiral bevel gear, the large spiral bevel gear changes the transmission direction of the force and drives the wheel to rotate, the driving spiral bevel gear is provided with a main spiral bearing and an oil seal, the main spiral bearing and the oil seal are externally provided with a main transmission shell, the main transmission shell is provided with a plurality of oil grooves for lubricating the main spiral bearing and the oil seal, flexible spacer sleeves are arranged between the inner rings of the main spiral bearing, and the differential case is provided with a differential assembly with a locking function.

[0011] Further, the oil grooves comprise a lubricating oil groove one and a lubricating oil groove two, the lubricating oil groove one is connected to the position of the main spiral bearing, and the lubricating oil groove one introduces oil to lubricate the main spiral bearing, and the lubricating oil groove two is connected between the oil seal and the main spiral bearing, and the lubricating oil groove two introduces oil to lubricate the space between the main spiral bearing and the oil seal.

[0012] Further, the lubricating oil groove one and the lubricating oil groove two are located on the two sides of the main transmission shell, and the lubricating oil groove one and the lubricating oil groove two are both spiral oil groove structures, the oil inlet of the lubricating oil groove one and the lubricating oil groove two is higher than the oil outlet, and the oil inlet of the lubricating oil groove one and the lubricating oil groove two is higher than the horizontal working condition oil level.

[0013] Further, the differential assembly comprises a one-way shaft, a small bevel gear connected to the one-way shaft, a half shaft gear in engagement with the small bevel gear, and the one-way shaft is connected with the differential case, the differential assembly further comprises a locking unit connected to the differential case and located outside the half shaft gear.

[0014] Further, the locking unit comprises a differential gear sleeve and a differential piston that are sequentially located outside the differential case in the axial direction, and a thrust bearing is arranged between the differential gear sleeve and the differential piston, the differential gear sleeve is provided with an inner spline, the differential case is provided with an outer spline, and the differential case comprises a return spring, when differential locking is needed, the differential gear sleeve is axially moved towards the one-way shaft by the differential piston, at this time, the inner spline and the outer spline are combined to realize differential locking, and when differential locking is not needed, the differential piston stops moving and the return spring separates the inner spline and the outer spline.

[0015] Further, the differential housing is provided with a differential bearing, and a driving oil passage is formed in the differential bearing seat of the differential bearing and communicated with the differential piston; the driving oil passage comprises a straight oil passage and an inclined oil passage communicated with the lower side of the straight oil passage; a limiting sleeve is arranged between the differential housing and the differential piston, and an oil outlet of the inclined oil passage forms a driving oil cavity with the differential piston, the differential bearing seat and the limiting sleeve.

[0016] Further, a plurality of end surface oil grooves are uniformly distributed on the end surface of the limiting sleeve close to the driving oil cavity, and the inclined oil passage guides the oil into the driving oil cavity, and the end surface oil grooves assist the oil to pass between the end surface of the differential piston and the limiting sleeve and provide axial thrust for the differential piston.

[0017] Further, a bevel gear gasket is arranged between the bevel gear and the differential housing, and the bevel gear gasket is a steel structure; a plurality of heat dissipation grooves are arranged on the bevel gear gasket.

[0018] Further, the driving spiral bevel gear is connected with an input flange below the oil seal, and a locking nut connected with the driving spiral bevel gear is arranged below the input flange; the flexible spacer sleeve comprises a supporting section, and the thickness and inner diameter parameters of the supporting section are determined by the tightening torque of the locking nut and the gap range between the main spiral bearing.

[0019] Further, the flexible spacer sleeve comprises a top supporting section arranged on the two radial sides of the supporting section, and the top supporting section is arranged on the end surface of the bearing inner ring of the main spiral bearing; the supporting section is an arc structure protruding away from the driving spiral bevel gear; and a deformation cavity is formed between the supporting section and the driving spiral bevel gear.

[0020] Compared with the prior art, the present application can achieve the following beneficial effects:

[0021] 1. The present application can solve the problem of poor lubrication of the driving bolt bearing position, which leads to damage of the bearing and oil seal in the high-speed running environment, by introducing oil through the oil groove.

[0022] 2. The present application can solve the problem of oil backflow into the housing, which cannot be stored in the bearing and oil seal, leading to insufficient lubrication and heat dissipation of the bearing and oil seal in uphill and downhill working conditions, by adopting the spiral oil groove design.

[0023] 3. The hydraulic differential lock structure introduced in the present application can effectively improve the vehicle's overall passability in ground conditions with large differences in ground adhesion.

[0024] 4. The present application uses a flexible spacer sleeve with greater stiffness to replace the traditional adjusting spacer, and the appropriate stiffness of the flexible spacer sleeve can meet the requirements of bearing clearance and tightening torque, solving the complex problem of adjusting bearing clearance.

[0025] 5、The application uses common steel to replace copper material to make bevel gear gasket, adopts and increases surface groove process, can solve the wear resistance problem in contact friction process, and greatly reduces the cost. BRIEF DESCRIPTION OF DRAWINGS

[0026] Figure 1 It is the overall structure schematic diagram of engineering machinery drive axle main transmission assembly provided according to the embodiment of the application;

[0027] Figure 2 It is Figure 1 The partial enlarged view of A in figure 1;

[0028] Figure 3 It is Figure 1 The partial enlarged view of B in figure 1;

[0029] Figure 4 It is the structure schematic diagram of limiting sleeve provided according to the embodiment of the application;

[0030] Figure 5 It is Figure 1 The partial enlarged view of C in figure 1;

[0031] Figure 6 It is the structure schematic diagram of flexible spacer sleeve provided according to the embodiment of the application;

[0032] Figure 7 It is the structure schematic diagram of lubricating oil groove provided according to the embodiment of the application;

[0033] Figure 8 It is the structure schematic diagram of bevel gear gasket provided according to the embodiment of the application.

[0034] The reference signs in the drawings include: differential gear housing 1, driving spiral bevel gear 2, large spiral bevel gear 3, main spiral bearing 4, main spiral bearing one 5, main spiral bearing two 6, oil seal 7, flexible spacer sleeve 8, lubricating oil groove one 9, lubricating oil groove two 10, straight axle 11, small bevel gear 12, half axle gear 13, differential gear sleeve 14, differential piston 15, thrust bearing 16, inner spline 17, outer spline 18, reset spring 19, differential gear bearing 20, differential gear bearing seat 21, driving oil channel 22, straight oil channel 23, inclined oil channel 24, limiting sleeve 25, end face oil groove 26, driving oil cavity 27, bevel gear gasket 28, heat dissipation groove 29, input flange 30, locking nut 31, support section 32, top support section 33, deformation cavity 34, main transmission housing 35, elastic baffle 36, elastic sealing ring 37, adjusting sleeve 38, rectangular cavity 39, sector cavity 40. DETAILED DESCRIPTION

[0035] In the following, the application will be described in detail with reference to the accompanying drawings. Figures 1-8Embodiments of the present application are described. In the following description, the same components are denoted by the same reference numerals. In the case of the same reference numerals, their names and functions are also the same. Therefore, detailed descriptions thereof will not be repeated.

[0036] In order to make the objectives, technical solutions and advantages of the present application clearer, the following further describes the present application with reference to the accompanying drawings and specific embodiments. It should be understood that the specific embodiments described herein are merely used to explain the present application and do not constitute a limitation on the present application. Figures 1-8 In order to make the objectives, technical solutions and advantages of the present application clearer, the following further describes the present application with reference to the accompanying drawings and specific embodiments. It should be understood that the specific embodiments described herein are merely used to explain the present application and do not constitute a limitation on the present application.

[0037] An engineering machinery drive axle main transmission assembly, as shown in Figure 1 , comprises a differential case 1, a driving spiral bevel gear 2 and a large spiral bevel gear 3 engaged with each other, the large spiral bevel gear 3 is connected with the differential case 1, the driving spiral bevel gear 2 is engaged below the large spiral bevel gear 3, the driving spiral bevel gear 2 and the large spiral bevel gear 3 are 90° staggered shaft structures, Figure 1 , wherein N is radial and M is axial, the driving spiral bevel gear 2 transmits force to the large spiral bevel gear 3, the large spiral bevel gear 3 changes the transmission direction of the force and drives the wheel to rotate, Figure 1 , wherein L line is the axial center line of the differential case 1, the wheel is located on both sides of L.

[0038] As shown in Figure 1 , the driving spiral bevel gear 2 is connected with an input flange 30 below the oil seal 7, the input flange 30 is connected with a power output, the driving force is output to the input flange 30 by the power output, the input flange 30 transmits the driving force to the driving spiral bevel gear 2, and the driving force is transmitted to the large spiral bevel gear 3 by the driving spiral bevel gear 2, the large spiral bevel gear 3 rotates with the differential case 1 and the output shaft inside the differential case 1, and the wheels are connected on both sides of the driving shaft to realize the rotation of the wheels.

[0039] As shown in Figure 1 , Figure 5 to Figure 7 , the driving spiral bevel gear 2 is provided with a main spiral bearing 4 and an oil seal 7, the main spiral bearing 4 and the oil seal 7 are externally provided with a main transmission housing 35, the main spiral bearing 4 and the oil seal 7 are assembled and fixed on the main transmission housing 35, and the main transmission housing 35 is provided with an oil groove group for lubricating the main spiral bearing 4 and the oil seal 7. The oil groove group comprises lubricating oil groove one 9 and lubricating oil groove two 10, the lubricating oil groove one 9 is communicated to the position of the main spiral bearing 4, and the oil introduced by the lubricating oil groove one 9 is used to lubricate the main spiral bearing 4, and the lubricating oil groove two 10 is communicated between the oil seal 7 and the main spiral bearing 4, and the oil introduced by the lubricating oil groove two 10 is used to lubricate between the main spiral bearing 4 and the oil seal 7. The main spiral bearing 4 comprises symmetrically arranged main spiral bearing one 5 and main spiral bearing two 6, as shown in Figure 5As shown, the lubricating oil groove one 9 introduces oil to continue lubricating the main helical bearing one 5 and the main helical bearing two 6, and the lubricating oil groove two 10 introduces oil to lubricate between the main helical bearing two 6 and the oil seal 7.

[0040] As shown in the drawings, Figure 7 The lubricating oil groove one 9 and the lubricating oil groove two 10 are respectively located on both sides of the main transmission housing 35, and the lubricating oil groove one 9 and the lubricating oil groove two 10 are both spiral oil groove structures. The oil inlet K1 of the lubricating oil groove one 9 and the lubricating oil groove two 10 is higher than the oil outlet K2, and the oil inlet K1 of the lubricating oil groove one 9 and the lubricating oil groove two 10 is higher than the horizontal working condition oil level P. The introduction of the oil groove group makes the driving bolt bearing position well lubricated, so that the main helical bearing 4 and the oil seal 7 can remain stable in the harsh high-speed running environment, so that the spiral oil groove can block the oil backflow to the inside of the housing, and the product damage caused by the oil remaining in the bearing and the oil seal can be avoided. The main helical bearing 4 and the oil seal 7 can be fully lubricated and cooled.

[0041] As shown in the drawings, Figure 1 , Figure 5 , Figure 6 The flexible spacer sleeve 8 is arranged between the bearing inner rings of the main helical bearing one 5 and the main helical bearing two 6. The flexible spacer sleeve 8 includes a support section 32, and the thickness and inner diameter parameters of the support section 32 are determined by the tightening torque of the lock nut 31 and the gap range between the main helical bearing 4. The flexible spacer sleeve 8 includes a top support section 33 located on both sides of the support section 32 in the radial direction. The top support section 33 is arranged on the bearing inner ring end face of the main helical bearing 4 and supports the bearing inner ring end face of the main helical bearing 4. The support section 32 is an arc-shaped structure protruding away from the driving helical bevel gear 2. The flexible spacer sleeve 8 is provided with a deformation cavity 34 between the support section 32 and the driving helical bevel gear 2. The deformation cavity 34 includes a rectangular cavity 39 arranged at the top support section 33 and a fan-shaped cavity 40 arranged at the support section 32.

[0042] As shown in the drawings, Figure 1As shown, the input flange 30 is provided below with a locking nut 31 connected with the driving spiral bevel gear 2, the locking nut 31 contacts the lower end of the input flange 30, the locking nut 31 is threadedly connected with the lower end of the driving spiral bevel gear, when the locking nut 31 is tightened, the input flange 30 will be pushed upward to the main spiral bearing 4, which will affect the play range between the main spiral bearing one 5 and the main spiral bearing two 6, at this time, the supporting section 32 of the flexible spacer sleeve 8 is compressed, the arc-shaped supporting section 32 can better bear and provide a reverse supporting force, and cooperate with the tightening torque of the locking nut 31 to give the bearing inner ring of the main spiral bearing one 5 and the main spiral bearing two 6 a radial supporting force, so as to control the play range between the main spiral bearing one 5 and the main spiral bearing two 6 within a reasonable range, at the same time, the deformation cavity 34 can provide a deformation space for the contraction of the flexible spacer sleeve 8 with a flexible structure while the flexible spacer sleeve 8 is bearing, and the cooperation of the fan-shaped cavity 40 and the rectangular cavity 39 can ensure the bearing stiffness of the flexible spacer sleeve 8 while providing a suitable deformation space for the flexible spacer sleeve 8.

[0043] When adjusting the related components on the driving spiral bevel gear 2, two requirements need to be met at the same time, one is to give the driving spiral bevel gear 2 a tightening torque, and at the same time, the play between the main spiral bearing one 5 and the main spiral bearing two 6 on the driving spiral bevel gear 2 needs to be controlled, the bearing inner ring of the main spiral bearing two 6 is pushed upward, without the flexible spacer sleeve 8, under a suitable torque, the main spiral bearing one 5 and the main spiral bearing two 6 will be compressed to death so that there is no gap, the flexible spacer sleeve 8 in the embodiment can lock the tightening torque of the locking nut 31, and at the same time, the play of the main spiral bearing one 5 and the main spiral bearing two 6 can be met.

[0044] As shown, Figures 1 to 3 The differential assembly with locking function is arranged in the differential housing 1, the differential assembly includes a pin shaft 11, a pinion 12 connected to the pin shaft 11, and a half shaft gear 13 meshing with the pinion 12. The pin shaft 11 is connected with the differential housing 1 and clamped by the differential housing 1, the driving force is transmitted to the large spiral bevel gear 3 by the driving spiral bevel gear 2, the large spiral bevel gear 3 transmits the driving force to the differential housing 1, the differential housing 1 rotates with the pin shaft 11, the pin shaft 11 drives the pinion 12 to rotate, the pinion 12 drives the half shaft gear 13 meshing therewith to move, and the half shaft gear 13 outputs the driving force to the two wheel edges through the spline.

[0045] A bevel gear 12 is provided with a bevel gear gasket 28 between the bevel gear 12 and the differential housing 1, the bevel gear gasket 28 is a steel structure, and a plurality of heat dissipation grooves 29 are provided on the bevel gear gasket 28. The ordinary steel material is used to replace the traditional copper material bevel gear gasket 28, which can save production cost while ensuring the use performance. The heat dissipation grooves 29 can be used to store lubricating oil, which can solve the problem of lubrication and heat dissipation during high-speed operation. The bevel gear gasket 28 has high wear resistance, smooth sliding friction and small friction coefficient. Through the automatic sliding property of copper, the friction coefficient can be reduced.

[0046] The differential assembly further comprises a lock unit connected to the differential housing 1 and located outside the half shaft gear 13, the lock unit comprises a differential gear sleeve 14 and a differential piston 15 which are sequentially located on the axial outside of the differential housing 1 from inside to outside, a thrust bearing 16 is provided between the differential gear sleeve 14 and the differential piston 15, and the axial movement of the differential piston 15 can drive the differential gear sleeve 14 to move axially through the thrust bearing 16. Because the differential piston 15 and the differential gear sleeve 14 will rotate relatively during movement, the thrust bearing 16 between the differential piston 15 and the differential gear sleeve 14 plays a role of bearing axial force and converting relative sliding friction into rolling friction during this process.

[0047] The differential gear sleeve 14 is provided with an inner spline 17, and the differential housing 1 is provided with an outer spline 18. The differential housing 1 includes a return spring 19. When differential locking is needed, the differential gear sleeve 14 is pushed by the differential piston 15 to move axially towards the straight shaft 11, at which time the inner spline 17 and the outer spline 18 are combined to realize differential locking. When differential locking is not needed, the differential piston 15 stops moving and the return spring 19 separates the inner spline 17 from the outer spline 18. When the adhesion of the two wheel edges differs greatly, or one wheel is stuck in the mud and keeps rotating, while the other wheel cannot get power output, the differential locking function can lock the differential function of the differential, so that the other wheel edge can get power, which can solve the problem that power can only be output from one side.

[0048] The differential housing 1 is provided with a differential bearing 20, and the differential bearing seat 21 of the differential bearing 20 is provided with a driving oil channel 22 communicated with the differential piston 15. The driving oil channel 22 includes a straight oil channel 23 and a inclined oil channel 24 communicated with the lower side of the straight oil channel 23. The straight oil channel 23 is formed downward from the upper end of the differential bearing seat 21, and the inclined oil channel 24 is formed upward and toward the lower end of the straight oil channel 23 from the lower end of the differential bearing seat 21. The design of the inclined oil channel 24 is based on the limited space of the oil channel on the differential bearing seat 21, in order to match the space of the oil channel on the differential bearing seat 21 and realize the driving requirements of the differential piston 15.

[0049] A limiting sleeve 25 is arranged between the differential housing 1 and the differential piston 15. The oil outlet of the inclined oil passage 24 and the differential piston 15, the differential bearing seat 21 and the limiting sleeve 25 form a driving oil cavity 27. Figure 4 As shown in the drawings, the end face of the limiting sleeve 25 close to the driving oil cavity 27 is uniformly provided with a plurality of end face oil grooves 26. The inclined oil passage 24 introduces oil into the driving oil cavity 27, and the end face oil grooves 26 assist the oil to pass between the end face of the differential piston 15 and the limiting sleeve 25 and provide axial thrust for the differential piston 15. Figure 4 As shown in the drawings, the end face of the limiting sleeve 25 is designed with a ring of end face oil grooves 26. The design of the ring of end face oil grooves 26 facilitates the introduction of oil between the limiting sleeve 25 and the differential piston 15 to push the differential piston 15 to move axially.

[0050] Although the embodiments of the present application have been shown and described above, it should be understood that the above embodiments are exemplary and should not be construed as limiting the present application. Those skilled in the art can make changes, modifications, replacements and variations to the above embodiments within the scope of the present application.

[0051] The specific embodiments of the present application described above do not constitute a limitation on the scope of protection of the present application. Any various other corresponding changes and modifications made according to the technical concept of the present application shall be included in the scope of protection of the claims of the present application.

Claims

1. An engineered machine drive axle main drive assembly, characterized by, The differential housing (1), the driving helical bevel gear (2) and the large helical bevel gear (3) are meshed with each other, the large helical bevel gear (3) is connected with the differential housing (1), the driving helical bevel gear (2) transmits the force to the large helical bevel gear (3), the large helical bevel gear (3) changes the transmission direction of the force and drives the wheel to rotate; the driving helical bevel gear (2) is provided with the main helical bearing (4) and the oil seal (7), the main helical bearing (4) and the oil seal (7) are provided with the main transmission housing (35) outside, the main transmission housing (35) is provided with the oil groove group for lubricating the main helical bearing (4) and the oil seal (7); the flexible spacer (8) is arranged between the inner rings of the main helical bearing (4); the differential assembly with the locking function is arranged in the differential housing (1); the oil groove group comprises the lubricating oil groove one (9) and the lubricating oil groove two (10); the lubricating oil groove one (9) is communicated to the position of the main helical bearing (4), and the oil introduced by the lubricating oil groove one (9) is used for lubricating the main helical bearing (4); the lubricating oil groove two (10) is communicated between the oil seal (7) and the main helical bearing (4), and the oil introduced by the lubricating oil groove two (10) is used for lubricating between the main helical bearing (4) and the oil seal (7); the differential assembly comprises the one axle (11), the small bevel gear (12) connected to the one axle (11), and the half shaft gear (13) meshed with the small bevel gear (12), and the one axle (11) is connected with the differential housing (1); the differential assembly further comprises the lock unit connected to the differential housing (1) and located outside the half shaft gear (13); the lock unit comprises the differential gear sleeve (14) and the differential piston (15) sequentially arranged from inside to outside on the axial outside of the differential housing (1), and the thrust bearing (16) is arranged between the differential gear sleeve (14) and the differential piston (15); the differential gear sleeve (14) is provided with the inner spline (17), the differential housing (1) is provided with the outer spline (18), and the differential housing (1) comprises the return spring (19); when the differential locking is needed, the differential gear sleeve (14) is axially moved towards the one axle (11) by the differential piston (15), at this time, the inner spline (17) and the outer spline (18) are combined to realize the differential locking; when the differential locking is not needed, the differential piston (15) stops moving, and the return spring (19) separates the inner spline (17) and the outer spline (18).

2. The main drive assembly of the construction machine drive axle according to claim 1, characterized in that, The lubricating oil groove one (9) and the lubricating oil groove two (10) are located on the two sides of the main transmission housing (35), the lubricating oil groove one (9) and the lubricating oil groove two (10) are all spiral oil groove structures; the oil inlet of the lubricating oil groove one (9) and the lubricating oil groove two (10) is higher than the oil outlet, and the oil inlet of the lubricating oil groove one (9) and the lubricating oil groove two (10) is higher than the horizontal working condition oil liquid plane.

3. The main drive assembly of claim 1, wherein, The differential housing (1) is provided with a differential bearing (20), and a differential bearing seat (21) of the differential bearing (20) is provided with a driving oil channel (22) communicated with the differential piston (15); the driving oil channel (22) comprises a straight oil channel (23) and a slant oil channel (24) communicated with the lower side of the straight oil channel (23); a limiting sleeve (25) is arranged between the differential housing (1) and the differential piston (15), and an oil outlet of the slant oil channel (24) forms a driving oil cavity (27) with the differential piston (15), the differential bearing seat (21) and the limiting sleeve (25).

4. The main drive assembly of claim 3, wherein, A plurality of end surface oil grooves (26) are uniformly distributed on the end surface of the limiting sleeve (25) close to the driving oil cavity (27), the slant oil channel (24) introduces oil into the driving oil cavity (27), the oil is guided to the end surface between the differential piston (15) and the limiting sleeve (25) by the end surface oil grooves (26), and the differential piston (15) is provided with an axial thrust.

5. The main drive assembly of claim 4, wherein, The bevel gear spacer (28) is arranged between the bevel gear (12) and the differential housing (1), and the bevel gear spacer (28) is a steel structure; a plurality of heat dissipation grooves (29) are arranged on the bevel gear spacer (28).

6. The main drive assembly of the construction machine drive axle according to claim 5, characterized in that, The driving spiral bevel gear (2) is connected with an input flange (30) below the oil seal (7), and a locking nut (31) connected with the driving spiral bevel gear (2) is arranged below the input flange (30); the flexible spacer sleeve (8) comprises a supporting section (32), and the thickness and inner diameter parameters of the supporting section (32) are determined by the tightening torque of the locking nut (31) and the gap range between the main spiral bearing (4).

7. The main drive assembly of the construction machine drive axle according to claim 6, characterized in that, The flexible spacer sleeve (8) comprises a top supporting section (33) arranged on the two radial sides of the supporting section (32), the top supporting section (33) is arranged on the bearing inner ring end surface of the main spiral bearing (4), the supporting section (32) is an arc structure protruding away from the driving spiral bevel gear (2), and a deformation cavity (34) is arranged between the supporting section (32) and the driving spiral bevel gear (2) on the flexible spacer sleeve (8).

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