Engineering machinery drive axle main transmission assembly

Abstract

The invention relates to the technical field of engineering machinery transmission parts, in particular to an engineering machinery drive axle main transmission assembly which comprises a differential shell, a driving spiral bevel gear and a large spiral bevel gear, the driving spiral bevel gear and the large spiral bevel gear are meshed with each other, the large spiral bevel gear is connected with the differential shell, and force is transmitted to the large spiral bevel gear through the driving spiral bevel gear. The large spiral bevel gear changes the transmission direction of force and drives wheels to operate, 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 the main transmission shell, the main transmission shell is provided with an oil groove set for lubricating the main spiral bearing and the oil seal, a flexible spacer bush is arranged between inner rings of the main spiral bearing, and the flexible spacer bush is connected with the main spiral bevel gear. A differential assembly with a locking function is arranged in the differential shell. According to the scheme, the whole machine trafficability under complex road conditions can be improved, the manufacturability in the assembly process is optimized, and the assembly cost and the part cost are reduced.

Description

Technical Field

[0001] The invention relates to the technical field of engineering machinery transmission parts, and specifically provides a main transmission assembly of an engineering machinery drive axle. Background Art

[0002] Construction machinery is an important part of the equipment industry, and is mainly used in defense construction projects, transportation construction, energy industry construction, raw material industry construction such as production mines, agriculture, forestry and water conservancy construction, industrial and civil construction, urban construction, environmental protection and other fields. The drive axle assembly is an important component of construction machinery, mainly used for transmission power and load-bearing weight. The drive axle assembly transmits the power provided by the engine to the wheel side of the vehicle, thereby driving the vehicle 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 construction machinery, and its performance directly affects the operating efficiency and safety of construction machinery.

[0003] As an important part of the drive axle assembly, the main drive of the drive axle is mainly composed of helical gear pairs, differential assemblies and other components. Its main function in the drive axle assembly is to increase torque and change the direction of force transmission. The traditional main drive of the drive axle of construction machinery has the following shortcomings: 1. Poor lubrication effect and unreasonable lubrication design of the active bolt bearing position will result in insufficient lubrication and heat dissipation of the bearings and oil seals in harsh high-speed operation environments; it may also cause the oil to flow back into the housing when the whole machine is working uphill or downhill, and cannot be retained in the bearings and oil seals, resulting in insufficient lubrication and heat dissipation of the bearings and oil seals under these conditions, causing damage.

[0004] 2. The traditional differential has the characteristic of differentiating speed but not force, which makes the structure of the differential unsuitable for ground conditions with large differences in ground adhesion.

[0005] 3. The active helical gear of some differentials is subjected to cantilever structure force, so it is necessary to meet the requirements of bearing clearance control while having sufficient bolt tightening force. However, it is complicated to adjust the bearing clearance with gaskets.

[0006] 4. Planetary gear gaskets are mostly made of copper, which will greatly increase the cost.

[0007] In summary, how to design a main transmission assembly of a drive axle of engineering machinery with good lubrication effect, which can ensure the passability of the whole machine under various road conditions, solve the complex problem of adjusting bearing clearance, and reduce costs is a problem that needs to be solved urgently. Summary of the invention

[0008] In order to solve the above problems, the present invention provides a main transmission assembly of a drive axle of an engineering machinery, which can solve the problems of poor lubrication, poor passability of the whole machine when the ground adhesion difference is large, complex bearing clearance and high cost.

[0009] The present invention provides a main transmission assembly of a driving axle of an engineering machinery, which specifically comprises a differential housing, a driving spiral bevel gear and a large spiral bevel gear meshing with each other, wherein the large spiral bevel gear is connected to the differential housing, and the driving spiral bevel gear transmits force to the large spiral bevel gear, and the large spiral bevel gear changes the transmission direction of the force and drives the wheels to rotate; a main spiral bearing and an oil seal are arranged on the driving spiral bevel gear, a main transmission housing is arranged outside the main spiral bearing and the oil seal, and an oil groove group for lubricating the main spiral bearing and the oil seal is opened on the main transmission housing; a flexible spacer is arranged between the inner rings of the main spiral bearings; and a differential assembly with a locking function is arranged in the differential housing.

[0010] Furthermore, the oil groove group includes lubricating oil groove 1 and lubricating oil groove 2; lubricating oil groove 1 is connected to the main spiral bearing, and oil is introduced from lubricating oil groove 1 to lubricate the main spiral bearing; lubricating oil groove 2 is connected to the oil seal and the main spiral bearing, and oil is introduced from lubricating oil groove 2 to lubricate the main spiral bearing and the oil seal.

[0011] Furthermore, lubricating oil groove 1 and lubricating oil groove 2 are respectively located on both sides of the main transmission housing, and both lubricating oil groove 1 and lubricating oil groove 2 are spiral oil groove structures; the oil inlets of lubricating oil groove 1 and lubricating oil groove 2 are higher than the oil outlet, and the oil inlets of lubricating oil groove 1 and lubricating oil groove 2 are higher than the horizontal working oil level.

[0012] Furthermore, the differential assembly includes a straight shaft, a small bevel gear connected to the straight shaft, and a half-shaft gear meshing with the small bevel gear, and the straight shaft is connected to the differential housing; the differential assembly also includes a locking unit connected to the differential housing and located on the outside of the half-shaft gear.

[0013] Furthermore, the locking unit includes a differential sleeve and a differential piston which are located on the axial outer side of the differential housing from the inside to the outside, and a thrust bearing is provided between the differential sleeve and the differential piston; an internal spline is provided on the differential sleeve, and an external spline is provided on the differential housing, and a return spring is included in the differential housing; when differential locking is required, the differential sleeve is pushed by the differential piston to move axially toward the straight shaft, and at this time, the internal spline and the external spline are combined to realize differential locking; when differential locking is not required, the differential piston stops moving and the internal spline and the external spline are separated by the return spring.

[0014] Furthermore, a differential bearing is provided on the differential housing, and a driving oil channel connected to the differential piston is opened on the differential bearing seat of the differential bearing; the driving oil channel includes a straight oil channel and an inclined oil channel connected to the lower side of the straight oil channel; a limit sleeve is provided between the differential housing and the differential piston, and a driving oil chamber is formed between the oil outlet of the inclined oil channel and the differential piston, the differential bearing seat and the limit sleeve.

[0015] Furthermore, a plurality of end face oil grooves are evenly distributed on the end face of the limit sleeve close to the driving oil chamber, and the inclined oil channel introduces the oil into the driving oil chamber. The end face oil grooves assist the oil to flow between the end faces of the differential piston and the limit sleeve and provide axial thrust for the differential piston.

[0016] Furthermore, a bevel gear gasket is provided between the small bevel gear and the differential housing, and the bevel gear gasket is a steel structure; and a plurality of heat dissipation grooves are provided on the bevel gear gasket.

[0017] Furthermore, the active spiral bevel gear is connected to an input flange located below the oil seal, and a locking nut connected to the active spiral bevel gear is provided below the input flange; the flexible spacer includes a support section, and the thickness and inner diameter parameters of the support section are determined by the tightening torque of the locking nut and the clearance range between the main spiral bearings.

[0018] Furthermore, the flexible spacer includes top support sections located on both sides of the support section in the radial direction, the top support sections are placed on the end face of the inner ring of the main spiral bearing, the support section is an arc-shaped structure protruding toward the side away from the active spiral bevel gear, and a deformation cavity is opened on the flexible spacer between the support section and the active spiral bevel gear.

[0019] Compared with the prior art, the present invention can achieve the following beneficial effects: 1. The present invention can solve the problem of poor lubrication of the active bolt bearing position, which causes damage to the bearing and oil seal in a high-speed operation environment by adding an oil groove to introduce oil.

[0020] 2. The present invention adopts a spiral oil groove design to solve the problem that when the whole machine is working uphill or downhill, the oil flows back into the shell and cannot be retained in the bearings and oil seals, resulting in the bearings and oil seals not being able to obtain sufficient lubrication and heat dissipation under such conditions, thus causing damage.

[0021] 3. The present invention introduces a hydraulic differential lock structure, which can effectively improve the vehicle's overall trafficability under ground conditions with large differences in ground adhesion.

[0022] 4. The present invention adopts a flexible spacer with greater rigidity to replace the traditional adjustment spacer. The appropriate rigidity of the flexible spacer can simultaneously meet the requirements of bearing clearance and tightening torque, solving the complex problem of adjusting bearing clearance.

[0023] 5. The present invention adopts common steel to replace copper material to make bevel gear gaskets, and adopts and increases the process of surface grooves, which can solve the wear resistance problem in the contact friction process, and also greatly reduces the cost. BRIEF DESCRIPTION OF THE DRAWINGS

[0024] Figure 1 It is a schematic diagram of the overall structure of a main transmission assembly of a drive axle of an engineering machinery provided according to an embodiment of the present invention; Figure 2 yes Figure 1 A partial enlarged view of the middle A; Figure 3 yes Figure 1 A partial enlarged view of point B in the middle; Figure 4 is a schematic structural diagram of a limit sleeve provided according to an embodiment of the present invention; Figure 5 yes Figure 1 A partial enlarged view of point C in the middle; Figure 6 is a schematic structural diagram of a flexible spacer provided according to an embodiment of the present invention; Figure 7 is a schematic structural diagram of a lubricating oil tank provided according to an embodiment of the present invention; Figure 8 is a schematic structural diagram of a bevel gear gasket provided according to an embodiment of the present invention.

[0025] The accompanying drawings include: differential housing 1, active spiral bevel gear 2, large spiral bevel gear 3, main spiral bearing 4, main spiral bearing 1 5, main spiral bearing 2 6, oil seal 7, flexible spacer 8, lubricating oil groove 1 9, lubricating oil groove 2 10, straight shaft 11, small bevel gear 12, half-shaft gear 13, differential gear sleeve 14, differential piston 15, thrust bearing 16, internal spline 17, external spline 18, return spring 19, differential bearing 20, differential bearing seat 21, drive oil channel 22, straight oil channel 23, oblique oil channel 24, limit sleeve 25, end face oil groove 26, drive 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 retaining ring 36, elastic sealing ring 37, adjustment sleeve 38, rectangular cavity 39, fan-shaped cavity 40. DETAILED DESCRIPTION

[0026] In the following, reference will be made to the Figure 1-8 Embodiments of the present invention are described. In the following description, the same modules are represented by the same reference numerals. In the case of the same reference numerals, their names and functions are also the same. Therefore, the detailed description thereof will not be repeated.

[0027] In order to make the purpose, technical solutions and advantages of the present invention more clearly understood, the following Figure 1-8 It should be understood that the specific embodiments described herein are only used to explain the present invention and do not constitute a limitation of the present invention.

[0028] A main transmission assembly of a drive axle of an engineering machinery, such as Figure 1 As shown, it includes a differential case 1, a driving spiral bevel gear 2 and a large spiral bevel gear 3 that mesh with each other, the large spiral bevel gear 3 is connected to the differential case 1, the driving spiral bevel gear 2 meshes below the large spiral bevel gear 3, and the driving spiral bevel gear 2 and the large spiral bevel gear 3 are a 90° staggered axis structure. Figure 1 N is radial, M is axial, the active spiral bevel gear 2 transmits the force to the large spiral bevel gear 3, the large spiral bevel gear 3 changes the direction of force transmission and drives the wheels to rotate. Figure 1 The middle L line is the axial center line of the differential housing 1, and the wheels are located on both sides of L.

[0029] like Figure 1 As shown, the active spiral bevel gear 2 is connected to an input flange 30 located below the oil seal 7, and the input flange 30 is connected to the power output member, and the power output member outputs the driving force to the input flange 30, and the input flange 30 then transmits the driving force to the active spiral bevel gear 2, and the active spiral bevel gear 2 then transmits the driving force to the large spiral bevel gear 3, and the large spiral bevel gear 3 rotates with the differential housing 1 and the output shaft inside it, and the wheels are connected to both sides of the drive shaft, so as to realize the operation of the wheels.

[0030] like Figure 1 , Figures 5 to 7 As shown, the active spiral bevel gear 2 is provided with a main spiral bearing 4 and an oil seal 7, and a main transmission housing 35 is provided outside the main spiral bearing 4 and the oil seal 7. The main spiral bearing 4 and the oil seal 7 are assembled and fixed on the main transmission housing 35, and an oil groove group for lubricating the main spiral bearing 4 and the oil seal 7 is opened on the main transmission housing 35. The oil groove group includes a lubricating oil groove 1 9 and a lubricating oil groove 2 10. The lubricating oil groove 1 9 is connected to the main spiral bearing 4, and oil is introduced from the lubricating oil groove 1 9 to lubricate the main spiral bearing 4. The lubricating oil groove 2 10 is connected to the oil seal 7 and the main spiral bearing 4, and oil is introduced from the lubricating oil groove 2 10 to lubricate the main spiral bearing 4 and the oil seal 7. The main spiral bearing 4 includes a main spiral bearing 1 5 and a main spiral bearing 2 6 which are symmetrically arranged, as shown in FIG. Figure 5 As shown, the lubricating oil groove 1 9 introduces oil to continue lubricating the main spiral bearing 1 5 and the main spiral bearing 2 6 , and the lubricating oil groove 2 10 introduces oil to lubricate between the main spiral bearing 2 6 and the oil seal 7 .

[0031] like Figure 7As shown, the lubricating oil groove 1 9 and the lubricating oil groove 2 10 are respectively located on both sides of the main transmission housing 35, and the lubricating oil groove 1 9 and the lubricating oil groove 2 10 are both spiral oil groove structures, and the oil inlet K1 of the lubricating oil groove 1 9 and the lubricating oil groove 2 10 are both higher than the oil outlet K2, and the oil inlet K1 of the lubricating oil groove 1 9 and the lubricating oil groove 2 10 are both higher than the oil plane P of the horizontal working condition. The introduction of the oil groove group makes the active bolt bearing position well lubricated, so that the main spiral bearing 4 and the oil seal 7 can maintain stable use in a harsh high-speed operation environment, so that in the working conditions of the whole machine uphill and downhill, the spiral oil groove can prevent the oil from flowing back to the inside of the housing, and will not remain in the bearing and the oil seal to cause product damage, which can ensure that the main spiral bearing 4 and the oil seal 7 can be fully lubricated and heat-dissipated.

[0032] like Figure 1 , Figure 5 , Figure 6 As shown, a flexible spacer 8 is provided between the inner rings of the main spiral bearing 1 5 and the main spiral bearing 2 6. The flexible spacer 8 includes a support section 32. The thickness and inner diameter parameters of the support section 32 are determined by the tightening torque of the locking nut 31 and the clearance range between the main spiral bearings 4. The flexible spacer 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 placed on the end face of the inner ring of the main spiral bearing 4 and is supported on the end face of the inner ring of the main spiral bearing 4. The support section 32 is an arc-shaped structure protruding toward the side away from the active spiral bevel gear 2. A deformation cavity 34 located between the support section 32 and the active spiral bevel gear 2 is provided on the flexible spacer 8. The deformation cavity 34 includes a rectangular cavity 39 opened at the top support section 33 and a fan-shaped cavity 40 opened at the support section 32.

[0033] like Figure 1 As shown, a locking nut 31 connected to the active spiral bevel gear 2 is provided below the input flange 30, and the locking nut 31 contacts the lower end of the input flange 30. The locking nut 31 is threadedly connected to the lower end of the active spiral bevel gear. When the locking nut 31 is tightened, the input flange 30 will be pushed upward toward the main spiral bearing 4, which will affect the clearance range between the main spiral bearing 1 5 and the main spiral bearing 2 6. At this time, the support section 32 of the flexible spacer 8 is compressed, and the support section 32 of the arc structure can better bear the load and provide reverse support force, and cooperate with the tightening torque of the locking nut 31 to give the inner rings of the main spiral bearing 1 5 and the main spiral bearing 2 6 a radial support force, so as to control the clearance range between the main spiral bearing 1 5 and the main spiral bearing 2 6 within a reasonable range. At the same time, when the flexible spacer 8 is bearing, the deformation cavity 34 can provide a deformation space for the contraction of the flexible spacer 8 of the flexible structure. The cooperation of the fan-shaped cavity 40 and the rectangular cavity 39 can provide a suitable deformation space for the flexible spacer 8 while ensuring the bearing stiffness of the flexible spacer 8.

[0034] When adjusting the relevant components on the active spiral bevel gear 2, two requirements need to be met at the same time. One is to give the active spiral bevel gear 2 a tightening torque, and at the same time to control the clearance between the main spiral bearing 1 5 and the main spiral bearing 2 6 on the active spiral bevel gear 2. The inner ring of the bearing of the main spiral bearing 2 6 is pushed upward. When there is no flexible spacer 8, under the appropriate torque, the main spiral bearing 1 5 and the main spiral bearing 2 6 will be crushed to death without a gap. In this embodiment, the above-mentioned flexible spacer 8 can lock the tightening torque of the nut 31, and at the same time can meet the clearance between the main spiral bearing 1 5 and the main spiral bearing 2 6.

[0035] like Figures 1 to 3 As shown, a differential assembly with a locking function is arranged in the differential housing 1, and the differential assembly includes a straight shaft 11, a small bevel gear 12 connected to the straight shaft 11, and a side gear 13 meshing with the small bevel gear 12. The straight shaft 11 is connected to the differential housing 1 and clamped by the differential housing 1. After the active spiral bevel gear 2 transmits the driving force to the large spiral bevel gear 3, the large spiral bevel gear 3 transmits the driving force to the differential housing 1. The differential housing 1 rotates with the straight shaft 11, the straight shaft 11 drives the small bevel gear 12 to operate, and the small bevel gear 12 drives the side gear 13 meshing with it to move, and the side gear 13 outputs the driving force to the two wheel edges through the spline.

[0036] A bevel gear gasket 28 is provided between the small bevel gear 12 and the differential housing 1. The bevel gear gasket 28 is a steel structure. A plurality of heat dissipation grooves 29 are provided on the bevel gear gasket 28. Ordinary steel is used to replace the traditional copper bevel gear gasket 28, which can save production costs while ensuring the performance. The heat dissipation grooves 29 can be used to store lubricating oil to solve the heat dissipation problem of lubrication during high-speed operation. The bevel gear gasket 28 has high wear resistance, smoother sliding friction, and a smaller friction coefficient. The friction coefficient can be reduced through the automatic sliding property of copper.

[0037] The differential assembly also includes a locking unit connected to the differential housing 1 and located on the outside of the half-shaft gear 13. The locking unit includes a differential sleeve 14 and a differential piston 15, which are located on the axial outside of the differential housing 1 from the inside to the outside. A thrust bearing 16 is provided between the differential sleeve 14 and the differential piston 15. The axial movement of the differential piston 15 can push the differential sleeve 14 to move axially through the thrust bearing 16. Because the differential piston 15 and the differential sleeve 14 will rotate relative to each other during the movement, the thrust bearing 16 between the differential piston 15 and the differential sleeve 14 plays a role in bearing the axial force and converting the sliding friction of the relative movement into rolling friction in this process.

[0038] 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 required, the differential gear sleeve 14 is pushed by the differential piston 15 to move axially toward the straight shaft 11. At this time, the inner spline 17 and the outer spline 18 are combined to achieve differential locking. When differential locking is not required, the differential piston 15 stops moving and the inner spline 17 and the outer spline 18 are separated by the return spring 19. When the adhesion of the two wheel sides is relatively different, or one wheel is stuck in the mud, the wheel will keep 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 side can get power, which can solve the problem that power can only be output from one side.

[0039] A differential bearing 20 is provided on the differential housing 1, and a driving oil passage 22 connected to the differential piston 15 is provided on the differential bearing seat 21 of the differential bearing 20; the driving oil passage 22 includes a straight oil passage 23 and an inclined oil passage 24 connected to the lower side of the straight oil passage 23, the straight oil passage 23 is opened downward from the upper end of the differential bearing seat 21, and the inclined oil passage 24 is opened from the lower end of the differential bearing seat 21 obliquely upward toward the lower end of the straight oil passage 23, and the design of the inclined oil passage 24 is based on the limited space for opening the oil passage on the differential bearing seat 21, in order to both cooperate with the opening space range for opening the oil passage on the differential bearing seat 21 and realize the driving requirements of the differential piston 15.

[0040] A limiting sleeve 25 is provided between the differential housing 1 and the differential piston 15, and a driving oil chamber 27 is formed between the oil outlet of the inclined oil passage 24 and the differential piston 15, the differential bearing seat 21, and the limiting sleeve 25. Figure 4 As shown, the end surface of the limit sleeve 25 near the driving oil chamber 27 is evenly distributed with a plurality of end surface oil grooves 26. The inclined oil passage 24 introduces the oil into the driving oil chamber 27. The end surface oil grooves 26 assist the oil to flow between the end surfaces of the differential piston 15 and the limit sleeve 25, and provide axial thrust for the differential piston 15. Figure 4 As shown, a circle of end surface oil groove 26 is designed on the end surface of the limit sleeve 25. The design of the whole circle of end surface oil groove 26 facilitates the comprehensive introduction of oil between the limit sleeve 25 and the differential piston 15 to push the differential piston 15 to move axially. The differential assembly can realize the differential speed of the left and right wheels, and automatically adjust the output speed of the left and right wheels according to the different speeds of the left and right wheels.

[0041] Although the embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and cannot be understood as limiting the present invention. Those skilled in the art may change, modify, replace and modify the above embodiments within the scope of the present invention.

[0042] The above specific implementations of the present invention do not constitute a limitation on the protection scope of the present invention. Any other corresponding changes and modifications made based on the technical concept of the present invention should be included in the protection scope of the claims of the present invention.

Claims

1. A main transmission assembly of a drive axle of an engineering machinery, characterized in that: The invention comprises a differential housing (1), a driving spiral bevel gear (2) and a large spiral bevel gear (3) meshing with each other, the large spiral bevel gear (3) being connected to the differential housing (1), the driving spiral bevel gear (2) transmitting force to the large spiral bevel gear (3), the large spiral bevel gear (3) changing the transmission direction of the force and driving the wheels to rotate; a main spiral bearing (4) and an oil seal (7) are provided on the driving spiral bevel gear (2), a main transmission housing (35) is provided outside the main spiral bearing (4) and the oil seal (7), an oil groove group for lubricating the main spiral bearing (4) and the oil seal (7) is provided on the main transmission housing (35); a flexible spacer (8) is provided between the inner rings of the main spiral bearing (4); and a differential assembly with a locking function is provided in the differential housing (1).

2. The main transmission assembly of the engineering machinery drive axle according to claim 1, characterized in that: The oil groove group comprises a lubricating oil groove 1 (9) and a lubricating oil groove 2 (10); the lubricating oil groove 1 (9) is connected to the main spiral bearing (4), and oil is introduced from the lubricating oil groove 1 (9) to lubricate the main spiral bearing (4); the lubricating oil groove 2 (10) is connected to between the oil seal (7) and the main spiral bearing (4), and oil is introduced from the lubricating oil groove 2 (10) to lubricate the main spiral bearing (4) and the oil seal (7).

3. The main transmission assembly of the engineering machinery drive axle according to claim 2, characterized in that: The lubricating oil groove 1 (9) and the lubricating oil groove 2 (10) are respectively located on both sides of the main transmission housing (35), and the lubricating oil groove 1 (9) and the lubricating oil groove 2 (10) are both spiral oil groove structures; the oil inlets of the lubricating oil groove 1 (9) and the lubricating oil groove 2 (10) are both higher than the oil outlet, and the oil inlets of the lubricating oil groove 1 (9) and the lubricating oil groove 2 (10) are both higher than the oil level under horizontal working conditions.

4. The main transmission assembly of the engineering machinery drive axle according to claim 1, characterized in that: The differential assembly comprises a straight shaft (11), a small bevel gear (12) connected to the straight shaft (11), and a half-shaft gear (13) meshing with the small bevel gear (12); the straight shaft (11) is connected to the differential housing (1); the differential assembly also comprises a locking unit connected to the differential housing (1) and located outside the half-shaft gear (13).

5. The main transmission assembly of the engineering machinery drive axle according to claim 4, characterized in that: The locking unit comprises a differential gear sleeve (14) and a differential piston (15) which are sequentially located on the axial outer side of the differential housing (1) from the inside to the outside, and a thrust bearing (16) is provided between the differential gear sleeve (14) and the differential piston (15); an internal spline (17) is provided on the differential gear sleeve (14), an external spline (18) is provided on the differential housing (1), and a return spring (19) is included in the differential housing (1); when differential locking is required, the differential gear sleeve (14) is pushed by the differential piston (15) to move axially in the direction of the straight shaft (11), and at this time, the internal spline (17) and the external spline (18) are combined to realize differential locking; when differential locking is not required, the differential piston (15) stops moving and the internal spline (17) is separated from the external spline (18) by the return spring (19).

6. The main transmission assembly of the engineering machinery drive axle according to claim 5, characterized in that: The differential housing (1) is provided with a differential bearing (20), and a driving oil passage (22) communicating with the differential piston (15) is provided on a differential bearing seat (21) of the differential bearing (20); the driving oil passage (22) comprises a straight oil passage (23) and an oblique oil passage (24) communicating with a lower side of the straight oil passage (23); a limiting sleeve (25) is provided between the differential housing (1) and the differential piston (15), and a driving oil chamber (27) is formed between an oil outlet of the oblique oil passage (24), the differential piston (15), the differential bearing seat (21), and the limiting sleeve (25).

7. The main transmission assembly of the engineering machinery drive axle according to claim 6, characterized in that: A plurality of end surface oil grooves (26) are evenly distributed on the end surface of the limiting sleeve (25) on the side close to the driving oil chamber (27); the inclined oil passage (24) introduces oil into the driving oil chamber (27); the end surface oil grooves (26) assist the oil to flow between the end surfaces of the differential piston (15) and the limiting sleeve (25) that match each other, and provide axial thrust for the differential piston (15).

8. The engineering machinery drive axle main transmission assembly according to claim 7, characterized in that: A bevel gear gasket (28) is provided between the small 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).

9. The engineering machinery drive axle main transmission assembly according to claim 1, characterized in that: The active spiral bevel gear (2) is connected to an input flange (30) located below the oil seal (7), and a locking nut (31) connected to the active spiral bevel gear (2) is provided below the input flange (30); the flexible spacer (8) comprises a support section (32), and the thickness and inner diameter parameters of the support section (32) are determined by the tightening torque of the locking nut (31) and the clearance range between the main spiral bearing (4).

10. The main transmission assembly of the engineering machinery drive axle according to claim 9, characterized in that: The flexible spacer (8) comprises top support sections (33) located on both radial sides of the support section (32); the top support sections (33) are placed on the end surface of the inner ring of the main spiral bearing (4); the support section (32) is an arc-shaped structure protruding toward a side away from the active spiral bevel gear (2); and a deformation cavity (34) is provided on the flexible spacer (8) between the support section (32) and the active spiral bevel gear (2).

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