CN111623101B - Clean long-life type inter-axle differential mechanism structure assembly - Google Patents
Clean long-life type inter-axle differential mechanism structure assembly Download PDFInfo
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- CN111623101B CN111623101B CN202010452690.XA CN202010452690A CN111623101B CN 111623101 B CN111623101 B CN 111623101B CN 202010452690 A CN202010452690 A CN 202010452690A CN 111623101 B CN111623101 B CN 111623101B
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- 238000009434 installation Methods 0.000 claims description 7
- 230000000295 complement effect Effects 0.000 claims description 6
- 238000005461 lubrication Methods 0.000 claims description 5
- 238000004140 cleaning Methods 0.000 claims description 3
- 239000007769 metal material Substances 0.000 claims description 3
- 239000003921 oil Substances 0.000 abstract description 22
- 239000000463 material Substances 0.000 abstract description 7
- 230000003749 cleanliness Effects 0.000 abstract description 4
- 238000005299 abrasion Methods 0.000 abstract description 3
- 230000000694 effects Effects 0.000 abstract description 3
- 239000012208 gear oil Substances 0.000 abstract description 3
- 230000007797 corrosion Effects 0.000 abstract description 2
- 238000005260 corrosion Methods 0.000 abstract description 2
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 6
- 229910052742 iron Inorganic materials 0.000 description 3
- 239000010687 lubricating oil Substances 0.000 description 3
- 239000003638 chemical reducing agent Substances 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000002893 slag Substances 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/048—Type of gearings to be lubricated, cooled or heated
- F16H57/0482—Gearings with gears having orbital motion
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/048—Type of gearings to be lubricated, cooled or heated
- F16H57/0493—Gearings with spur or bevel gears
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Details Of Gearings (AREA)
- Retarders (AREA)
Abstract
The invention discloses a clean long-life type inter-axle differential mechanism structure assembly which is characterized by comprising an input shaft, a cross shaft, a planet wheel, a rear half axle wheel, a driving cylindrical gear, an input shaft rear bearing, a thrust bearing, a driving cylindrical gear bushing, a shaft difference shell, an oil retainer ring, a rear half axle wheel thrust washer, a middle axle shell reduction and a rear half axle wheel bushing; the thrust bearing structure between the input shaft and the driving cylindrical gear is set, and the thrust washer with the semi-through groove structure between the input shaft and the rear half shaft wheel is set, so that friction damage at two positions is effectively reduced; the driving cylindrical gear bushing limiting end face is additionally arranged, so that the problem that the bushing is separated frequently in the current after-sales market is effectively solved, the anti-rotation limiting end face of the shaft difference shell is additionally arranged, and the large-angle rotation of the shaft difference shell is avoided, and the problem that an elongated oil retainer frequently interferes with a bearing outer ring or a middle bridge shell reduction for improving the oil receiving effect is solved; the gear bushing and the oil retainer made of nonmetallic materials have the advantages of high temperature resistance, corrosion resistance and friction resistance, and the abrasion scraps have very limited influence on the cleanliness of the gear oil and are light in weight.
Description
Technical Field
The invention relates to the technical field of heavy truck automobile axles, in particular to a clean long-life inter-axle differential mechanism structure assembly.
Background
The inter-axle differential assembly is an important part on the main speed reducer assembly of the middle axle of the drive axle, and not only plays a role in transmitting torque transmitted by an input shaft to a driven cylindrical gear of the middle axle and a through shaft, but also has the function of generating differential speed between the driven cylindrical gear and the through shaft so as to ensure the normal running of a vehicle.
In the conventional inter-axle differential assembly structure, a common gasket structure is usually arranged between a driving cylindrical gear and an input shaft, and the gasket is severely worn due to the existence of uninterrupted differential speed of the driving cylindrical gear and the input shaft; the traditional back half axle wheel thrust washer and the back half axle wheel are of a slotless structure, so that lubricating oil is difficult to enter a matching surface, and also because of the existence of uninterrupted differential speed between an input shaft and the back half axle wheel, abnormal abrasion faults of the washer frequently occur, and the washer is designed to be of a double-sided open groove structure for improving lubrication, but fracture faults are caused due to strength problems; the driving cylindrical gear is not provided with a limiting end face of a bushing in structure, the fault that the bushing is separated frequently due to the complex loading condition of the driving wheel, and the fault that the oil retainer interferes with the reduction of the middle axle shell or the movement of the bearing behind the input axle occurs due to the fact that the axle differential shell rotates in a large angle in the running process of the vehicle because of the fact that the axle differential shell is not provided with an anti-rotation limiting boss; in addition, in the traditional inter-axle differential assembly, the driving cylindrical gear bushing, the rear half axle wheel bushing and the oil retainer are all made of metal materials, the positions of the two bushings determine that the two bushings are always worn, the oil retainer occasionally has a wear problem, the cleanliness of the gear oil by worn scrap iron and iron slag of the three is not affected little, the service life of other parts in the main assembly is reduced, and moreover, the oil retainer is not loaded, made into metal parts and increased in weight.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide a clean long-life type inter-axle differential mechanism structure assembly.
The technical scheme provided by the invention is as follows: the utility model provides a clean long-life type interaxial differential mechanism structure assembly which is characterized in that the structure assembly comprises an input shaft, a cross shaft, a planet wheel, a rear half-axle wheel, a driving cylindrical gear, an input shaft rear bearing, a thrust bearing, a driving cylindrical gear bushing, a shaft difference shell, a oil retainer ring, a rear half-axle wheel thrust washer, a middle axle shell and a rear half-axle wheel bushing; the inner diameter of the cross shaft is the same as the outer diameter of the cross shaft matching position of the input shaft, radial limit is realized by spline matching of the inner diameter of the cross shaft and the outer diameter of the cross shaft matching position, and the input shaft drives the cross shaft to freely rotate; the inner diameter of the planet wheel is the same as the outer diameter of the cross shaft, the planet wheel and the cross shaft are assembled together through shaft holes in a matching way, the planet wheel freely rotates on the cross shaft, and the number of the planet wheels is 4; the inner diameter of the spherical surface of the shaft difference shell is the same as the outer diameter of the spherical surface of the planet wheel, the inner diameter and the outer diameter of the spherical surface are matched and assembled together, the shaft difference shell floats on the planet wheel, and relative to the planet wheel, the shaft difference shell is effectively limited in translation along the axial direction and the radial direction except for rotating relative to the common spherical center of the shaft difference shell and the planet wheel; the outer diameter of the mounting spigot of the oil retainer is the same as the inner diameter of the mounting position of the oil retainer of the shaft difference shell, and the mounting spigot and the inner diameter of the mounting position of the oil retainer are fixed together by the interference fit of the shaft holes and the propping limit of the parallel end surfaces; the outer diameter of the rear half shaft wheel bushing is the same as the inner diameter of the mounting position of the rear half shaft wheel bushing, and the rear half shaft wheel bushing are assembled and fixed together through shaft hole interference fit; the inner diameter of the rear half shaft wheel bushing is the same as the outer diameter of the matching position of the rear half shaft wheel of the input shaft, and the rear half shaft wheel bushing and the input shaft are matched and assembled together through the shaft hole, so that the rear half shaft wheel and the rear half shaft wheel bushing can freely rotate on the input shaft; the outer diameter of the rear half axle wheel bearing mounting position is the same as the inner diameter of the bearing inner ring of the rear bearing of the input shaft, and the rear half axle wheel bearing mounting position and the inner diameter of the bearing inner ring are propped against and fixed together through shaft hole matching and the parallel end surfaces of the rear half axle wheel and the bearing inner ring; the outer diameter of the bearing outer ring of the rear bearing of the input shaft is the same as the inner diameter of the mounting position of the middle axle shell reduction bearing, the bearing outer ring and the parallel end surface of the middle axle shell reduction bearing are propped against and fixed together through shaft hole matching, and the rear half shaft wheel freely rotates on the middle axle shell reduction through the rear bearing of the input shaft; the rear half shaft wheel and the conical teeth of the planetary wheel are equal in modulus, the pitch cone angles are complementary, the axial leads are perpendicular to each other, the pitch cone points are coincident, and the mutual meshing and relative rotation relation of the straight-tooth conical teeth are realized by meshing together; the outer diameter of the driving cylindrical gear bushing is the same as the inner diameter of the bushing mounting position of the driving cylindrical gear, and the driving cylindrical gear bushing and the bushing mounting position are assembled and fixed together through shaft hole interference fit; the inner diameter of the driving cylindrical gear bushing is the same as the outer diameter of the driving cylindrical gear matching position of the input shaft, and the driving cylindrical gear bushing and the input shaft are matched and assembled together through the shaft hole, so that the driving cylindrical gear and the driving cylindrical gear bushing can freely rotate on the input shaft; the driving cylindrical gear and the conical teeth of the planetary gear are equal in modulus, the pitch cone angles are complementary, the axial leads are perpendicular to each other, the pitch cone points are coincident, and the meshing of the straight-tooth conical teeth and the relative rotation relationship are realized; the inner diameter of the rear half shaft wheel thrust washer is the same as the outer diameter of the rear half shaft wheel mounting position of the input shaft, the rear half shaft wheel thrust washer and the rear half shaft wheel mounting position are mounted together through shaft hole matching, the upper end face and the lower end face of the rear half shaft wheel thrust washer are respectively parallel to the corresponding matched end faces of the input shaft and the rear half shaft wheel, the rear half shaft wheel thrust washer and the rear half shaft wheel are propped against each other, the axial limiting of the input shaft is realized, and the rear half shaft wheel thrust washer and the rear half shaft wheel mounting position mutually rotate; the inner diameter of the thrust bearing is the same as the outer diameter of the driving cylindrical gear mounting position of the input shaft, the thrust bearing and the driving cylindrical gear mounting position are mounted together through shaft hole matching, the upper end face and the lower end face of the thrust bearing are parallel to the corresponding matching end faces of the input shaft and the driving cylindrical gear respectively, the thrust bearing, the driving cylindrical gear and the driving cylindrical gear are propped together and leave an axial gap of 0.8-1.2mm, and the axial limit of the driving cylindrical gear is realized while the meshing gap adjustment of the planet wheel, the rear half shaft wheel and the driving cylindrical gear is realized.
Further, the thrust bearing is a series of components for adjusting the gear clearance of the differential.
Further, the driving cylindrical gear is provided with an axle difference shell rotation preventing limit boss, the end face of the axle difference shell rotation preventing limit boss is parallel to the front end face of the axle difference shell, and the distance between the end face of the axle difference shell rotation preventing limit boss and the front end face of the axle difference shell is 0.8-1.0mm, so that the axle difference shell rotation preventing boss is used for limiting the rotation of the axle difference shell; the driving cylindrical gear is provided with an anti-falling limiting inner end face of the driving cylindrical gear bushing, the anti-falling limiting inner end face is parallel to the end face of the driving cylindrical gear bushing, and the diameter of an inner hole of the end face is between the inner diameter and the outer diameter of the driving cylindrical gear bushing and is used for limiting the axial direction of the driving cylindrical gear bushing so as to prevent falling.
Further, the rear half axle wheel thrust washer unilateral have half logical groove, 3 circumference equipartitions of quantity have logical groove with its complex rear half axle wheel's terminal surface, 4 circumference equipartitions of quantity, rear half axle wheel thrust washer does not have trough one side and rear half axle wheel contact cooperation, so not only avoided the stress concentration of rear half axle wheel thrust washer, still be convenient for work lubrication.
Furthermore, the driving cylindrical gear bushing, the oil retainer ring and the rear half shaft wheel bushing are all made of nonmetallic materials.
The beneficial effects of the invention are as follows: 1. the thrust bearing structure between the input shaft and the driving cylindrical gear effectively reduces friction damage among the input shaft, the driving cylindrical gear and the driving cylindrical gear; 2. the structural design of the single-side half through groove of the back half shaft gear thrust washer keeps a lubricating oil duct between the back half shaft gear thrust washer and an input shaft, and also avoids the problem of fracture frequently occurring in the conventional thin-wall washer through groove structure; the rear half shaft gear is additionally provided with a slotting structure, so that the lubrication effect between the rear half shaft gear and the thrust washer is effectively improved, and the friction damage is reduced; 3. the driving cylindrical gear bushing limiting end face is additionally arranged, so that the problem that the bushing is separated frequently in the current after-sales market is effectively solved, the anti-rotation limiting end face of the shaft difference shell is additionally arranged, and the large-angle rotation of the shaft difference shell is avoided, and the problem that an elongated oil retainer frequently interferes with a bearing outer ring or a middle bridge shell reduction for improving the oil receiving effect is solved; 4. the gear bushing and the oil retainer made of nonmetallic materials have the advantages of high temperature resistance, corrosion resistance and friction resistance, the influence of abrasion scraps on the cleanliness of the gear oil is very limited, the quality is light, and the market trend of industry light weight is met.
Drawings
FIG. 1 is a schematic diagram of the structure of the present invention;
FIG. 2 is a schematic illustration of the structure of the rear axle wheel thrust washer of the present invention;
fig. 3 is a schematic structural view of the rear half axle wheel of the present invention.
Detailed Description
For a better understanding and implementation, the present invention is described in detail below with reference to specific examples in conjunction with the accompanying drawings; the examples are given solely for the purpose of illustration and are not intended to limit the scope of the invention.
As shown in fig. 1, 2 and 3, a cleaning long-life type inter-axle differential mechanism structure assembly is composed of an input shaft 1, a cross shaft 2, a planet wheel 3, a rear half axle wheel 4, a driving cylindrical gear 5, an input shaft rear bearing 6, a thrust bearing 7, a driving cylindrical gear bushing 8, a shaft difference shell 9, an oil retainer 10, a rear half axle wheel thrust washer 11, a middle axle reduction shell 12 and a rear half axle wheel bushing 13, wherein the driving cylindrical gear bushing 8, the oil retainer 10 and the rear half axle wheel bushing 13 are all made of nonmetallic materials; the inner diameter of the cross shaft 2 is processed to be the same as the outer diameter of a cross shaft matching position of the input shaft 1, and the two parts are assembled together through spline matching to realize radial limit, so that the input shaft 1 can drive the cross shaft 2 to freely rotate; the inner diameter of the planet wheel 3 is processed to be the same as the outer diameter of the cross shaft 2, the planet wheel 3 and the cross shaft 2 are assembled together through shaft holes in a matching way, the planet wheel 3 can freely rotate on the cross shaft 2, and the number of the planet wheels 3 is 4; the spherical inner diameter of the shaft difference shell 9 is processed to be the same as the spherical outer diameter of the planetary gear 3, the spherical inner diameter and the spherical outer diameter are matched and assembled together, the shaft difference shell 9 floats on the planetary gear 3, and relative to the planetary gear 3, the shaft difference shell 9 can rotate relative to the common spherical center of the planetary gear 3, and translation along the axial direction and the radial direction is effectively limited; the inner diameter of the oil retainer mounting position of the shaft difference shell 9, which is processed by the outer diameter of the mounting spigot of the oil retainer 10, is the same, and the two are fixed together through interference fit of the shaft hole and propping up of mutually parallel end surfaces against limit assembly; the outer diameter of the rear half shaft wheel bushing 13 is processed to be the same as the inner diameter of the mounting position of the rear half shaft wheel 4 bushing, and the rear half shaft wheel bushing 13 and the rear half shaft wheel bushing are assembled and fixed together through shaft hole interference fit; the inner diameter of the rear half shaft wheel bushing 13 is processed to be the same as the outer diameter of the matching position of the rear half shaft wheel of the input shaft 1, and the rear half shaft wheel bushing 13 and the outer diameter of the matching position of the rear half shaft wheel of the input shaft 1 are matched and assembled together through the shaft hole, so that the rear half shaft wheel 4 and the rear half shaft wheel bushing 13 can freely rotate on the input shaft 1; the outer diameter of the bearing installation position of the rear half shaft wheel 4 is processed to be the same as the inner diameter of the bearing inner ring of the rear bearing 6 of the input shaft, and the rear half shaft wheel 4 and the bearing inner ring are fixedly assembled together through shaft hole matching and propping and leaning of the parallel end surfaces of the rear half shaft wheel 4 and the bearing inner ring; the outer diameter of the bearing outer ring of the rear bearing 6 of the input shaft is processed to be the same as the inner diameter of the bearing installation position of the middle axle reduction shell 12, and the bearing outer ring and the parallel end surface of the middle axle reduction shell 12 are assembled and fixed together through shaft hole matching and propping, so that the rear half shaft wheel 4 can freely rotate on the middle axle reduction shell 12 through the rear bearing 6 of the input shaft; the back half shaft wheel 4 and the conical teeth of the planetary wheel 3 are processed to be equal in modulus, the pitch cone angles are mutually complementary, the axis lines are mutually perpendicular and the pitch cone points are coincident during assembly, and the meshing together achieves the mutual meshing and relative rotation relationship of the straight-tooth conical teeth; the outer diameter of the driving cylindrical gear bushing 8 is processed to be the same as the inner diameter of the bushing mounting position of the driving cylindrical gear 5, and the driving cylindrical gear bushing 8 and the bushing mounting position are assembled and fixed together through shaft hole interference fit; the inner diameter of the driving cylindrical gear bushing 8 is processed to be the same as the outer diameter of the driving cylindrical gear matching position of the input shaft 1, and the driving cylindrical gear bushing 8 and the outer diameter of the driving cylindrical gear matching position of the input shaft 1 are matched and assembled together through the shaft hole, so that the driving cylindrical gear 5 and the driving cylindrical gear bushing 8 can freely rotate on the input shaft 1; the driving cylindrical gear 5 is provided with an axle difference shell rotation preventing limit boss 52, the end face of the axle difference shell rotation preventing limit boss 52 is parallel to the front end face of the axle difference shell 9, and the distance between the axle difference shell rotation preventing limit boss and the front end face of the axle difference shell 9 is 0.8-1.0mm, so that the axle difference shell 9 is used for rotation limitation; the driving cylindrical gear 5 is provided with an anti-falling limit inner end surface 51 for the driving cylindrical gear bushing 8, which is parallel to the end surface of the driving cylindrical gear bushing 8, and the diameter of the inner hole of the end surface is between the inner diameter and the outer diameter of the driving cylindrical gear bushing 8, so as to limit the axial direction of the driving cylindrical gear bushing 8 to prevent falling; the driving cylindrical gear 5 and the conical teeth of the planetary gears 3 are processed to be equal in modulus, the pitch cone angles are complementary, the axis lines are mutually perpendicular and the pitch cone points are coincident when the planetary gears are assembled, and the meshing of the straight-tooth conical teeth and the relative rotation are realized by meshing together; the rear half axle wheel thrust washer 11 is provided with half through grooves 111 on one side, 3 through grooves 41 are formed in the end face of the rear half axle wheel 4 matched with the half through grooves in a circumferentially uniform manner, and 4 through grooves are formed in the end face of the rear half axle wheel 4 in a circumferentially uniform manner, and one side of the rear half axle wheel thrust washer 11 without the grooves is in contact fit with the rear half axle wheel 4 during assembly, so that stress concentration of the rear half axle wheel thrust washer 11 is avoided, and working lubrication is facilitated; the inner diameter of the rear half shaft wheel thrust washer 11 is processed to be the same as the outer diameter of the rear half shaft wheel mounting position of the input shaft 1, the rear half shaft wheel thrust washer and the rear half shaft wheel mounting position are mounted together in a matched manner through a shaft hole, the upper end face and the lower end face of the rear half shaft wheel thrust washer are respectively parallel to the corresponding matched end faces of the input shaft 1 and the rear half shaft wheel 4, the rear half shaft wheel thrust washer and the rear half shaft wheel thrust washer are propped against each other, the axial limiting of the input shaft 1 is realized, and the rear half shaft wheel thrust washer can rotate mutually; the thrust bearing 7 is a group of components used for adjusting the gear clearance of the differential mechanism, the inner diameter of the thrust bearing 7 is processed to be the same as the outer diameter of the driving cylindrical gear mounting position of the input shaft 1, the thrust bearing 7 and the driving cylindrical gear mounting position are assembled together through shaft hole matching, the upper end face and the lower end face of the thrust bearing are respectively parallel to the corresponding matching end faces of the input shaft 1 and the driving cylindrical gear 5, the thrust bearing 7 and the driving cylindrical gear are propped together and leave an axial clearance of 0.8-1.2mm, the axial limit of the driving cylindrical gear 5 is realized while the meshing clearance adjustment of the planetary gear 3, the rear half shaft wheel 4 and the driving cylindrical gear 5 is realized, and the three components can mutually rotate; thus, the clean long-life inter-axle differential mechanism structure assembly is formed.
The invention relates to a clean long-life type inter-axle differential mechanism structure assembly, which is a necessary structure in a main speed reducer assembly of a drive axle, and when in operation, the front end of an input shaft 1 receives torque transmitted by a transmission shaft, and the rotation is transmitted to a cross shaft 2 through spline connection under the support of front and rear bearings of the input shaft (the front end of the input shaft is additionally provided with a front bearing); 4 planetary gears 3 assembled on the cross shaft 2, and a shaft difference housing 9 and a oil retainer 10 for assembling the planetary gears 3 and the cross shaft 2, all rotate together with the cross shaft 2; the planetary gear 3 can revolve around the input shaft 1 along with the cross shaft 2 and also can rotate on the cross shaft 2, so that the planetary gear is meshed with the bevel gear to realize the rotation of the driving cylindrical gear 5 and the rear half shaft wheel 4 around the input shaft 1 together, namely, the differential function is realized, and the adjustment of the fit clearance between the bevel gears in the differential is realized through the axial limit of a group of thickness series thrust bearings 7; the differential function is specifically embodied in: when the load of the structural assembly is the same as that of the connecting piece of the driving cylindrical gear 5 and the rear half shaft wheel 4, the planetary wheel 3 does not rotate, and when the load of the structural assembly is different from that of the connecting piece of the driving cylindrical gear 5 and the rear half shaft wheel 4, the planetary wheel 3 rotates to drive the driving cylindrical gear 5 and the rear half shaft wheel 4 to realize the rotation speed difference and the differential function;
In addition, due to the existence of the axle difference shell anti-rotation limiting boss 52 on the driving cylindrical gear 5, the free rotation swing of the axle difference shell 9 suspended on the planet wheel 3 is limited, so that the operation interference of the oil retainer 10 and the adjacent small clearance piece is avoided; the driving cylindrical gear 5 and the shaft difference shell 9 are subjected to heat treatment, so that the material hardness is high, and the driving cylindrical gear is suitable for being used as a limiting piece to effectively play a role in preventing rotation interference; the active cylindrical gear bushing 8 is easy to fall out due to complex loading condition of the active cylindrical gear 5, and the occurrence of the fault in actual working operation is avoided due to the existence of the falling-preventing limit inner end surface 51; the selection of the nonmetallic materials of the parts improves the damage of the worn scrap iron to the cleanliness of the lubricating oil when the original metallic materials are adopted, ensures the long-service-life operation of the inter-axle differential mechanism structure assembly, and is also good promotion and promotion for exploring and applying the nonmetallic materials in the field of automobile chassis while gradually reducing the weight of the product.
Claims (3)
1. The utility model provides a clean long-life type inter-axle differential mechanism structure assembly which is characterized in that, by input shaft (1), cross axle (2), planet wheel (3), back half axle wheel (4), initiative cylindrical gear (5), input shaft back bearing (6), footstep bearing (7), initiative cylindrical gear bush (8), axle difference shell (9), oil retainer (10), back half axle wheel thrust washer (11), intermediate axle subtract shell (12) and back half axle wheel bush (13); the inner diameter of the cross shaft (2) is the same as the outer diameter of the cross shaft matching position of the input shaft (1), radial limit is realized by spline matching of the inner diameter and the outer diameter, and the input shaft (1) drives the cross shaft (2) to freely rotate; the inner diameter of the planet wheel (3) is the same as the outer diameter of the cross shaft (2), the planet wheel (3) and the cross shaft (2) are assembled together through shaft holes in a matching way, the planet wheel (3) rotates freely on the cross shaft (2), and the number of the planet wheels (3) is 4 in total; the spherical inner diameter of the shaft difference shell (9) is the same as the spherical outer diameter of the planet wheel (3), the spherical inner diameter and the spherical outer diameter are assembled together in a matched manner, the shaft difference shell (9) floats on the planet wheel (3), and relative to the planet wheel (3), the shaft difference shell (9) is effectively limited in translation along the axial direction and the radial direction except for rotating relative to the common spherical center of the shaft difference shell and the planet wheel (3); the outer diameter of the mounting spigot of the oil retainer (10) is the same as the inner diameter of the oil retainer mounting position of the shaft difference shell (9), and the two are fixed together by the interference fit of the shaft hole and the propping limit of the parallel end surfaces; the outer diameter of the rear half shaft wheel bushing (13) is the same as the inner diameter of the mounting position of the rear half shaft wheel (4) bushing, and the rear half shaft wheel bushing are assembled and fixed together through shaft hole interference fit; the inner diameter of the rear half shaft wheel bushing (13) is the same as the outer diameter of the rear half shaft wheel matching position of the input shaft (1), and the rear half shaft wheel bushing and the outer diameter are matched and assembled together through the shaft hole, so that the rear half shaft wheel (4) and the rear half shaft wheel bushing (13) can freely rotate on the input shaft (1); the outer diameter of the bearing installation position of the rear half shaft wheel (4) is the same as the inner diameter of the bearing inner ring of the rear bearing (6) of the input shaft, and the bearing installation position and the inner diameter are matched through a shaft hole and are propped against and fixed with the parallel end surfaces of the bearing inner ring of the rear half shaft wheel (4); the outer diameter of the bearing outer ring of the rear bearing (6) of the input shaft is the same as the inner diameter of the bearing installation position of the middle axle reduction shell (12), the bearing outer ring and the parallel end surface of the middle axle reduction shell (12) are propped and fixed together through shaft hole matching, and the rear half shaft wheel (4) freely rotates on the middle axle reduction shell (12) through the rear bearing (6) of the input shaft; the rear half shaft wheel (4) and the planetary wheel (3) have equal taper tooth modulus, mutually complementary pitch cone angles, mutually perpendicular shaft axes and coincident pitch cone points, and are meshed together to realize the mutual meshing and relative rotation relationship of straight-tooth taper teeth; the outer diameter of the driving cylindrical gear bushing (8) is the same as the inner diameter of the bushing mounting position of the driving cylindrical gear (5), and the driving cylindrical gear bushing and the bushing mounting position are assembled and fixed together through shaft hole interference fit; the inner diameter of the driving cylindrical gear bushing (8) is the same as the outer diameter of the driving cylindrical gear matching position of the input shaft (1), and the driving cylindrical gear bushing and the outer diameter of the driving cylindrical gear matching position of the input shaft (1) are matched and assembled together through the shaft hole, so that the driving cylindrical gear (5) and the driving cylindrical gear bushing (8) can freely rotate on the input shaft (1); the driving cylindrical gear (5) and the conical teeth of the planetary gear (3) are equal in modulus, the pitch angles are complementary, the axial leads are mutually perpendicular, the pitch points are coincident, and the meshing and the relative rotation relationship of the straight-tooth conical teeth are realized; the inner diameter of the rear half shaft wheel thrust washer (11) is the same as the outer diameter of the rear half shaft wheel mounting position of the input shaft (1), the rear half shaft wheel thrust washer and the rear half shaft wheel mounting position are mounted together through shaft hole matching, the upper end face and the lower end face of the rear half shaft wheel thrust washer are parallel to the corresponding matching end faces of the input shaft (1) and the rear half shaft wheel (4) respectively, the rear half shaft wheel thrust washer and the rear half shaft wheel mounting position are propped against each other, the axial limiting of the input shaft (1) is realized, and the rear half shaft wheel thrust washer and the rear half shaft wheel mounting position mutually rotate; the inner diameter of the thrust bearing (7) is the same as the outer diameter of the driving cylindrical gear installation position of the input shaft (1), the thrust bearing and the driving cylindrical gear installation position are installed together through shaft holes in a matched mode, the upper end face and the lower end face of the thrust bearing are parallel to the corresponding matched end faces of the input shaft (1) and the driving cylindrical gear (5), the thrust bearing, the driving cylindrical gear and the driving cylindrical gear are propped against each other, an axial gap of 0.8-1.2mm is reserved between the thrust bearing, the driving cylindrical gear (5) and the driving cylindrical gear, and the axial limiting of the driving cylindrical gear (5) is realized while meshing gaps among the planet wheel (3), the rear half-shaft wheel (4) and the driving cylindrical gear (5) are adjusted;
the thrust bearing (7) is a group of components and is used for adjusting the gear clearance of the differential mechanism;
The driving cylindrical gear (5) is provided with an axle difference shell rotation preventing limit boss (52), the end face of the axle difference shell rotation preventing limit boss (52) is parallel to the front end face of the axle difference shell (9), and the distance between the axle difference shell and the front end face of the axle difference shell is 0.8-1.0mm, so that the axle difference shell (9) is used for rotation limitation; the driving cylindrical gear (5) is provided with an anti-falling limit inner end face (51) for the driving cylindrical gear bushing (8), the anti-falling limit inner end face is parallel to the end face of the driving cylindrical gear bushing (8), and the diameter of an inner hole of the end face is between the inner diameter and the outer diameter of the driving cylindrical gear bushing (8) and is used for limiting the axial direction of the driving cylindrical gear bushing (8) so as to prevent falling.
2. The cleaning and long-service-life type inter-axle differential mechanism structure assembly according to claim 1, wherein the rear half axle wheel thrust washer (11) is provided with half through grooves (111) on one side, 3 through grooves (41) are circumferentially uniformly distributed on the end face of the rear half axle wheel (4) matched with the rear half axle wheel thrust washer, 4 through grooves are circumferentially uniformly distributed on the end face of the rear half axle wheel thrust washer, and one side of the rear half axle wheel thrust washer (11) without grooves is in contact fit with the rear half axle wheel (4) during assembly, so that stress concentration of the rear half axle wheel thrust washer (11) is avoided, and working lubrication is facilitated.
3. The long-life cleaning differential mechanism structure assembly of claim 1, wherein said driving cylindrical gear bushing (8), oil retainer (10) and rear axle shaft wheel bushing (13) are all of non-metallic materials.
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| CN202010452690.XA CN111623101B (en) | 2020-05-26 | 2020-05-26 | Clean long-life type inter-axle differential mechanism structure assembly |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN205896130U (en) * | 2016-07-13 | 2017-01-18 | 中国第一汽车股份有限公司 | Medium -sized automobile rear drive main reducer assembly |
| WO2017198097A1 (en) * | 2016-05-20 | 2017-11-23 | 泗阳县勇士机械制造有限公司 | Variable torque limited slip differential and method for designing same |
| CN212455405U (en) * | 2020-05-26 | 2021-02-02 | 山东蓬翔汽车有限公司 | Clean long-life type interaxial differential mechanism structure assembly |
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2020
- 2020-05-26 CN CN202010452690.XA patent/CN111623101B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2017198097A1 (en) * | 2016-05-20 | 2017-11-23 | 泗阳县勇士机械制造有限公司 | Variable torque limited slip differential and method for designing same |
| CN205896130U (en) * | 2016-07-13 | 2017-01-18 | 中国第一汽车股份有限公司 | Medium -sized automobile rear drive main reducer assembly |
| CN212455405U (en) * | 2020-05-26 | 2021-02-02 | 山东蓬翔汽车有限公司 | Clean long-life type interaxial differential mechanism structure assembly |
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