Engineering machinery drive axle transmission system convenient for heat dissipation and lubrication

Abstract

The utility model relates to the technical field of engineering machinery transmission parts, in particular to an engineering machinery drive axle transmission system convenient for heat dissipation and lubrication, which comprises a driving spiral bevel gear and a large spiral bevel gear which are meshed with each other, a main spiral bearing and an oil seal are arranged between the main transmission shell and the driving spiral bevel gear; an oil groove group for lubricating the main spiral bearing and the oil seal is formed in the main transmission shell; the oil groove set comprises a first lubricating oil groove and a second lubricating oil groove, the first lubricating oil groove is communicated to the main spiral bearing, the second lubricating oil groove is communicated between the oil seal and the main spiral bearing, and the first lubricating oil groove and the second lubricating oil groove are each of a spiral oil groove structure. According to the scheme of the utility model, the problem that the bearing and the oil seal are damaged due to insufficient lubrication and heat dissipation in a high-speed operation environment caused by poor lubrication of the bearing can be solved.

Description

Technical Field

[0001] The utility model relates to the technical field of engineering machinery transmission parts, and specifically provides an engineering machinery drive axle transmission system which is convenient for heat dissipation and lubrication. Background Art

[0002] Construction machinery is a vital component of the equipment industry, primarily used in defense construction, transportation, energy, mining, and other raw material industries, agriculture, forestry, and water conservancy projects, industrial and civil construction, urban development, and environmental protection. The drive axle assembly is a crucial component in construction machinery, primarily responsible for transmitting power and carrying weight. It transmits engine power to the vehicle's wheels, driving it forward and backward. It also bears the weight and steering responsibilities of the vehicle. Therefore, the drive axle assembly plays a crucial role in construction machinery, and its performance directly impacts its operational efficiency and safety.

[0003] The main drive of the drive axle, as an important component of the drive axle assembly, is mainly composed of components such as a helical gear pair and a differential assembly. Its main function in the drive axle assembly is to increase torque and change the direction of force transmission. The main drive system of the traditional drive axle of engineering machinery has the following problems: 1) The lubrication effect of the active bolt bearing position is poor and the lubrication design is unreasonable, which will result in the bearings and oil seals not receiving sufficient lubrication and heat dissipation in harsh high-speed operating environments. It may also cause the oil to flow back into the interior of the housing when the entire machine is operating uphill or downhill, and it will not be retained in the bearings and oil seals, resulting in insufficient lubrication and heat dissipation of the bearings and oil seals under these operating conditions, causing damage. 2) Since the active helical gear of some differentials is a cantilever structure, it is necessary to meet the requirements of bearing clearance control while having sufficient bolt tightening force. However, adjusting the bearing clearance with shims is more complicated.

[0004] In summary, how to design a main transmission assembly for a drive axle of engineering machinery with good lubrication effect and capable of solving the complex problem of adjusting bearing clearance is an issue that needs to be solved urgently. Utility Model Content

[0005] In order to solve the above problems, the utility model provides an engineering machinery drive axle transmission system which is convenient for heat dissipation and lubrication, and can solve the problems of poor lubrication and complex bearing clearance.

[0006] The utility model provides a drive axle transmission system for engineering machinery that is convenient for heat dissipation and lubrication. Specifically, the system comprises an active spiral bevel gear and a large spiral bevel gear that mesh with each other. The outer side of the active spiral bevel gear comprises a main transmission housing. A main spiral bearing and an oil seal are comprised between the main transmission housing and the active spiral bevel gear. An oil groove group for lubricating the main spiral bearing and the oil seal is provided on the main transmission housing. The oil groove group comprises a first lubricating oil groove and a second lubricating oil groove. The first lubricating oil groove is connected to the main spiral bearing, and the second lubricating oil groove is connected to between the oil seal and the main spiral bearing.

[0007] Furthermore, the first lubricating oil groove and the second lubricating oil groove are both spiral oil groove structures.

[0008] Furthermore, the oil inlets of the lubricating oil tank 1 and the lubricating oil tank 2 are both higher than the oil outlet, and the oil inlets of the lubricating oil tank 1 and the lubricating oil tank 2 are both higher than the oil level under horizontal working conditions.

[0009] Furthermore, the first lubricating oil groove and the second lubricating oil groove are respectively located on both sides of the main transmission housing.

[0010] Furthermore, the main spiral bearing includes a main spiral bearing 1 and a main spiral bearing 2 that are symmetrically arranged, and a flexible spacer is provided between the inner rings of the main spiral bearing 1 and the main spiral bearing 2.

[0011] Furthermore, the driving spiral bevel gear is connected to an input flange located below the oil seal, and a locking nut connected to the driving spiral bevel gear is provided below the input flange.

[0012] Furthermore, the flexible spacer includes a support section, and the thickness and inner diameter parameters of the support section are set according to the tightening torque of the locking nut and the clearance range between the main spiral bearings.

[0013] Furthermore, the flexible spacer includes top support sections located on both sides of the support section in the radial direction, and the top support sections are placed on the end surface of the bearing inner ring between the main spiral bearing 1 and the main spiral bearing 2 6.

[0014] Furthermore, the supporting section is an arc-shaped structure that protrudes toward a side away from the driving spiral bevel gear.

[0015] Furthermore, a deformation cavity is provided on the flexible spacer and is located between the support section and the active spiral bevel gear. The deformation cavity includes a rectangular cavity provided at the top support section and a fan-shaped cavity provided at the support section.

[0016] Compared with the prior art, the present invention can achieve the following beneficial effects:

[0017] 1. The utility model solves the problem of poor lubrication of the active bolt bearing position, which causes damage to the bearing and oil seal in a harsh high-speed operation environment, by adding an oil groove to introduce oil.

[0018] 2. The utility model adopts a spiral oil groove design to solve the problem that when the whole machine is working in uphill or downhill conditions, the oil flows back into the shell and cannot be retained in the bearings and oil seals, resulting in insufficient lubrication and heat dissipation of the bearings and oil seals under such conditions, thus causing damage.

[0019] 3. The utility model 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. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1 This 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 utility model;

[0021] Figure 2 yes Figure 1 A partial enlarged view of point A in the middle;

[0022] Figure 3 yes Figure 1 A partial enlarged view of point B in the middle;

[0023] Figure 4 It is a structural schematic diagram of a limit sleeve provided according to an embodiment of the utility model;

[0024] Figure 5 yes Figure 1 A partial enlarged view of point C in the middle;

[0025] Figure 6 It is a structural schematic diagram of a flexible spacer provided according to an embodiment of the utility model;

[0026] Figure 7 It is a structural schematic diagram of a lubricating oil tank provided according to an embodiment of the utility model;

[0027] Figure 8 It is a structural schematic diagram of a bevel gear gasket provided according to an embodiment of the utility model.

[0028] 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 66, 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 chamber 27, bevel gear gasket 28, heat dissipation groove 29, input flange 30, locking nut 31, support section 32, top support section 33, deformation chamber 34, main transmission housing 35, elastic retaining ring 36, elastic sealing ring 37, adjustment sleeve 38, rectangular chamber 39, fan-shaped chamber 40. DETAILED DESCRIPTION

[0029] In the following, reference will be made to the Figure 1-8 The 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, their detailed description will not be repeated.

[0030] In order to make the purpose, technical solutions and advantages of this utility model more clear, 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.

[0031] 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, and the driving spiral bevel gear 2 meshes with the large spiral bevel gear 3 below. 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 radial transmission force to the large spiral bevel gear 3, and the large spiral bevel gear 3 converts the radial transmission force into axial transmission force and drives the wheels to rotate. Figure 1 The center L line is the axial center line of the differential housing 1, and the wheels are located on both sides of L.

[0032] like Figure 1As shown, the driving spiral bevel gear 2 is connected to an input flange 30 located below the oil seal 7. 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. The input flange 30 then transmits the driving force to the driving spiral bevel gear 2, and the driving spiral bevel gear 2 transmits the driving force to the large spiral bevel gear 3. The large spiral bevel gear 3 rotates with the differential case 1 and the output shaft inside it. The wheels are connected to both sides of the drive shaft to realize the operation of the wheels.

[0033] 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 on 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. 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 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 the 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 the 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 that are symmetrically arranged, as shown 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 the space between the main spiral bearing 2 6 and the oil seal 7.

[0034] like Figure 7 As shown, lubricating oil groove 1 9 and lubricating oil groove 2 10 are located on either side of the main transmission housing 35. Both lubricating oil groove 1 9 and lubricating oil groove 2 10 have spiral oil groove structures. The oil inlet K1 of lubricating oil groove 1 9 and lubricating oil groove 2 10 is higher than the oil outlet K2, and the oil inlet K1 of lubricating oil groove 1 9 and lubricating oil groove 2 10 is higher than the oil level P under horizontal operating conditions. The introduction of the oil groove group ensures good lubrication of the active bolt bearing position, ensuring that the main spiral bearing 4 and oil seal 7 can maintain stable operation in harsh high-speed operating environments. When the entire machine is operating in uphill or downhill conditions, the spiral oil grooves prevent oil from flowing back into the housing, preventing it from accumulating in the bearings and oil seals and causing product damage, ensuring that the main spiral bearing 4 and oil seal 7 are fully lubricated and heat dissipated.

[0035] like Figure 1 、 Figure 5 、 Figure 6As 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 top support sections 33 located on both sides of the support section 32 in the radial direction. The top support sections 33 are placed on the end faces of the inner rings of the main spiral bearing 4 and are supported on the end faces of the inner rings of the main spiral bearing 4. The support section 32 is an arc-shaped structure that protrudes toward the side away from the active spiral bevel gear 2. The flexible spacer 8 is provided with a deformation cavity 34 located between the support section 32 and the active spiral bevel gear 2. 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.

[0036] 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, thereby controlling 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 bears the load, 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 load-bearing stiffness of the flexible spacer 8.

[0037] 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 appropriate torque, the main spiral bearing 1 5 and the main spiral bearing 2 6 will be crushed to death so that there is no 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 of the main spiral bearing 1 5 and the main spiral bearing 2 6.

[0038] like Figures 1 to 3As shown, a differential assembly with a locking function is installed within the differential housing 1. The differential assembly includes a straight shaft 11, a small bevel gear 12 connected to the straight shaft 11, and side gears 13 meshing with the small bevel gear 12. The straight shaft 11 is connected to and clamped by the differential housing 1. After the driving 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, which drives the small bevel gear 12 to operate. The small bevel gear 12 drives the meshing side gears 13 to move. The side gears 13 output the driving force to the two wheel sides through splines.

[0039] 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.

[0040] The differential assembly also includes a locking unit connected to the differential housing 1 and located on the outside of the side gear 13. The locking unit includes a differential sleeve 14 and a differential piston 15, which are located axially outside 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 motion into rolling friction during this process.

[0041] The differential sleeve 14 is provided with internal splines 17, and the differential housing 1 is provided with external splines 18. A return spring 19 is included within the differential housing 1. When differential locking is required, the differential piston 15 pushes the differential sleeve 14 axially toward the straight shaft 11. At this point, the internal splines 17 and external splines 18 engage to achieve differential locking. When differential locking is no longer required, the differential piston 15 stops moving, and the return spring 19 separates the internal splines 17 and external splines 18. When the adhesion between the two wheel sides differs significantly, or when one wheel is stuck in mud, the wheel will continue to rotate while the other wheel will not receive power output. The differential lock function locks the differential function, allowing the other wheel side to receive power, thus resolving the problem of power output only coming from one side.

[0042] A differential bearing 20 is provided on the differential housing 1, and a drive oil passage 22 connected to the differential piston 15 is provided on the differential bearing seat 21 of the differential bearing 20; the drive 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 obliquely upward from the lower end of the differential bearing seat 21 toward the lower end of the straight oil passage 23. 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. It is provided in order to match the space range for opening the oil passage on the differential bearing seat 21 and to meet the driving requirements of the differential piston 15.

[0043] 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 uniformly distributed with multiple end surface oil grooves 26. The inclined oil channel 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, the end surface of the stop sleeve 25 is designed with a circle of end surface oil grooves 26. The design of the entire circle of end surface oil grooves 26 facilitates the comprehensive introduction of oil between the stop sleeve 25 and the differential piston 15 to propel the differential piston 15 axially. The differential assembly can achieve differential speed between the left and right wheels, automatically adjusting the output speed of the left and right wheels according to the difference in left and right wheel speeds.

[0044] 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 make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention.

[0045] The above specific embodiments of the present invention do not constitute a limitation on the scope of protection 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 scope of protection of the claims of the present invention.

Claims

1. A drive axle transmission system for engineering machinery that facilitates heat dissipation and lubrication, characterized in that: The invention comprises a driving spiral bevel gear (2) and a large spiral bevel gear (3) meshing with each other, the outer side of the driving spiral bevel gear (2) comprises a main transmission housing (35), a main spiral bearing (4) and an oil seal (7) are provided between the main transmission housing (35) and the driving spiral bevel gear (2), and an oil groove group for lubricating the main spiral bearing (4) and the oil seal (7) is provided on the main transmission housing (35); 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), the lubricating oil groove 2 (10) is connected to the oil seal (7) and the main spiral bearing (4); the lubricating oil groove 1 (9) and the lubricating oil groove 2 (10) are both spiral oil groove structures; 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); the main spiral bearing (4) includes a main spiral bearing 1 (5) and a main spiral bearing 2 (6) that are symmetrically arranged, and a flexible spacer (8) is provided between the bearing inner rings of the main spiral bearing 1 (5) and the main spiral bearing 2 (6).

2. The engineering machinery drive axle transmission system for heat dissipation and lubrication according to claim 1 is characterized in that: The oil inlets of the lubricating oil tank 1 (9) and the lubricating oil tank 2 (10) are both higher than the oil outlet, and the oil inlets of the lubricating oil tank 1 (9) and the lubricating oil tank 2 (10) are both higher than the oil level under horizontal working conditions.

3. The engineering machinery drive axle transmission system for heat dissipation and lubrication according to any one of claims 1-2, characterized in that: The driving 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 driving spiral bevel gear (2) is provided below the input flange (30).

4. The engineering machinery drive axle transmission system for heat dissipation and lubrication according to claim 3 is characterized in that: The flexible spacer (8) includes a support section (32), and the thickness and inner diameter parameters of the support section (32) are set according to the tightening torque of the locking nut (31) and the clearance range between the main spiral bearing (4).

5. The engineering machinery drive axle transmission system for heat dissipation and lubrication according to claim 4 is characterized in that: The flexible spacer (8) includes top support sections (33) located on both radial sides of the support section (32), and the top support sections (33) are placed on the end surface of the bearing inner ring between the main spiral bearing 1 (5) and the main spiral bearing 2 (6).

6. The engineering machinery drive axle transmission system for heat dissipation and lubrication according to claim 5 is characterized in that: The support section (32) is an arc-shaped structure that protrudes toward a side away from the active spiral bevel gear (2).

7. The engineering machinery drive axle transmission system for heat dissipation and lubrication according to claim 6 is characterized in that: The flexible spacer (8) is provided with a deformation cavity (34) located between the support section (32) and the active spiral bevel gear (2), and the deformation cavity (34) comprises a rectangular cavity (39) opened at the top support section (33) and a fan-shaped cavity (40) opened at the support section (32).

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