CN107387714A - A kind of limited-slip differential assembly and main reducing gear - Google Patents
A kind of limited-slip differential assembly and main reducing gear Download PDFInfo
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- CN107387714A CN107387714A CN201710456603.6A CN201710456603A CN107387714A CN 107387714 A CN107387714 A CN 107387714A CN 201710456603 A CN201710456603 A CN 201710456603A CN 107387714 A CN107387714 A CN 107387714A
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- 230000007246 mechanism Effects 0.000 claims abstract description 94
- 238000009434 installation Methods 0.000 claims description 19
- 238000005461 lubrication Methods 0.000 claims 1
- 239000003921 oil Substances 0.000 description 31
- 239000003638 chemical reducing agent Substances 0.000 description 10
- 238000010586 diagram Methods 0.000 description 5
- 239000010687 lubricating oil Substances 0.000 description 5
- 230000005540 biological transmission Effects 0.000 description 3
- 230000017525 heat dissipation Effects 0.000 description 2
- 230000001050 lubricating effect Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000006698 induction Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 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
- F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
- F16H48/11—Differential gearings with gears having orbital motion with orbital spur gears having intermeshing planet 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
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/22—Arrangements for suppressing or influencing the differential action, e.g. locking devices using friction clutches or brakes
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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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/17—Toothed wheels
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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
- F16H57/0421—Guidance of lubricant on or within the casing, e.g. shields or baffles for collecting lubricant, tubes, pipes, grooves, channels or the like
- F16H57/0424—Lubricant guiding means in the wall of or integrated with the casing, e.g. grooves, channels, holes
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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
- F16H57/045—Lubricant storage reservoirs, e.g. reservoirs in addition to a gear sump for collecting lubricant in the upper part of a gear case
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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
- F16H48/38—Constructional details
- F16H2048/385—Constructional details of the ring or crown gear
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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
- F16H57/0483—Axle or inter-axle differentials
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
Abstract
The invention provides a kind of limited-slip differential assembly and main reducing gear, the differential assembly includes：Spiral bevel gear, the spiral bevel gear are connected with differential mechanism right end cap, and the differential mechanism right end cap is connected with differential casing, and the differential casing is also connected with differential mechanism left end cap；Left planetary gear, the left planetary gear are arranged in the differential mechanism left end cap；Right planetary gear, the right planetary gear are arranged in the differential mechanism right end cap；Left half axle gear, the left half axle gear are arranged in the first gear mounting hole of described differential casing one end；Right axle shaft gear, the right axle shaft gear are arranged in the second gear mounting hole of the differential casing other end；First friction mechanism, first friction mechanism are arranged between the differential mechanism left end cap and the differential casing；Second friction mechanism, second friction mechanism are arranged between the differential mechanism right end cap and the differential casing.
Description
Technical Field
The invention belongs to the technical field of vehicle transmission, and particularly relates to a limited slip differential assembly and a main speed reducer.
Background
In a vehicle driveline, power is typically transferred to each wheel through a differential assembly. A differential is a device that allows the left and right wheels to rotate at different speeds. When the vehicle is on a smooth road surface, such as snow or ice, because the friction force of the tire is small and the rotation speed of the side gear on the slipping side in the differential mechanism is higher than that of the side gear on the non-slipping side, the wheel with the high rotation speed can rotate freely under the working condition, so that a large amount of driving torque is converted into tire slipping, and the non-slipping side cannot obtain driving force, and finally the vehicle cannot run out of the slipping area.
In order to prevent the wheel from skidding, the antiskid differential mechanism used in the prior art comprises a jaw differential mechanism, a Torsen differential mechanism, a friction plate type limited slip differential mechanism and the like. However, the above-mentioned differential is complex in structure and the limited slip capability does not meet the requirements of some heavy-duty high-throughput chassis, such as a special off-road vehicle chassis.
Based on the above, the present invention provides a limited slip differential assembly and a main reducer, so as to solve the above problems in the prior art.
Disclosure of Invention
Aiming at the problems in the prior art, the embodiment of the invention provides a limited slip differential assembly and a main speed reducer, which are used for solving the technical problems that an anti-slip differential in the prior art is complex in structure and insufficient in limited slip capacity.
The present invention provides a limited slip differential assembly, the differential assembly comprising:
the spiral bevel gear is connected with a right end cover of the differential, the right end cover of the differential is connected with a differential shell, and the differential shell is also connected with a left end cover of the differential;
a left planetary gear mounted in the differential left end cap;
a right planetary gear mounted in the differential right end cap;
a left side gear mounted in a first gear mounting hole at one end of the differential case;
the right half shaft gear is installed in a second gear installation hole in the other end of the differential shell;
a first friction mechanism mounted between the differential left end cap and the differential housing;
a second friction mechanism mounted between the differential right end cap and the differential housing; wherein,
the gear module of the left planetary gear and the gear module of the right planetary gear are 2.5-3.5; the number of teeth of the left planetary gear and the number of teeth of the right planetary gear are 6-8; the pressure angle between the left planetary gear and the right planetary gear is 20-30 degrees; the helical angle of the left planetary gear and the right planetary gear is 30-45 degrees.
In the above aspect, the left planetary gear includes:
a first planetary gear, a second planetary gear, a third planetary gear and a fourth planetary gear; the right planetary gear includes: a fifth planetary gear, a sixth planetary gear, a seventh planetary gear and an eighth planetary gear; wherein,
the first planetary gear, the second planetary gear, the third planetary gear and the fourth planetary gear are respectively installed in corresponding planetary gear installation holes in a left end cover of the differential mechanism;
the fifth planetary gear, the sixth planetary gear, the seventh planetary gear and the eighth planetary gear are respectively installed in corresponding planetary gear installation holes in the right end cover of the differential.
In the above solution, the first planetary gear is meshed with the fifth planetary gear; the second planetary gear is meshed with the sixth planetary gear; the third planetary gear is meshed with the seventh planetary gear; the fourth planetary gear is meshed with the eighth planetary gear;
the left side gear is meshed with the first planetary gear, the second planetary gear, the third planetary gear and the fourth planetary gear respectively;
the right half shaft gear is respectively meshed with the fifth planetary gear, the sixth planetary gear, the seventh planetary gear and the eighth planetary gear.
In the above aspect, the first friction mechanism includes: the friction plate comprises a first locking ring, a first outer friction plate, a first inner friction plate, a second outer friction plate, a second inner friction plate, a third outer friction plate and a third inner friction plate; wherein,
the first locking ring is connected with the left half shaft gear in a sliding mode;
the first outer friction disc, the first inner friction disc, the second outer friction disc, the second inner friction disc, the third outer friction disc and the third inner friction disc are sequentially arranged between the first locking ring and the differential shell in sequence;
the first outer friction disc, the second outer friction disc and the third outer friction disc are correspondingly installed in tooth-shaped installation holes reserved in the differential shell;
the involute splines of the first inner friction plate, the second inner friction plate and the third inner friction plate are matched and connected with the involute splines on the excircle of the first locking ring.
In the above aspect, the second friction mechanism includes: a second lock ring, a second outer friction disk, a fourth inner friction disk, a fifth outer friction disk, a fifth inner friction disk, a sixth outer friction disk and a sixth inner friction disk; wherein,
the second locking ring is connected with the right half shaft gear in a sliding manner;
the second outer friction disc, the fourth inner friction disc, the fifth outer friction disc, the fifth inner friction disc, the sixth outer friction disc and the sixth inner friction disc are sequentially arranged between the second lock ring and the differential shell in sequence;
the second outer friction disc, the fourth outer friction disc, the fifth outer friction disc and the sixth outer friction disc are correspondingly installed in tooth-shaped installation holes reserved in the differential shell;
the involute splines of the fourth inner friction plate, the fifth inner friction plate and the sixth inner friction plate are matched and connected with the involute splines on the excircle of the second locking ring.
In the scheme, the left end cover of the differential mechanism and the right end cover of the differential mechanism are both provided with the lubricating oil passing hole and the oil collecting pool.
In the above scheme, the differential is a parallel helical gear type differential.
In the above scheme, the left side gear and the right side gear are coaxial with the differential case.
In the above scheme, a deflection angle is formed between the left planetary gear mounting hole and the right planetary gear mounting hole.
The invention also provides a main speed reducer, which comprises the differential assembly.
The invention provides a limited slip differential assembly and a main speed reducer, wherein the differential assembly comprises: the spiral bevel gear is connected with a right end cover of the differential, the right end cover of the differential is connected with a differential shell, and the differential shell is also connected with a left end cover of the differential; a left planetary gear mounted in the differential left end cap; a right planetary gear mounted in the differential right end cap; a left side gear mounted in a first gear mounting hole at one end of the differential case; the right half shaft gear is installed in a second gear installation hole in the other end of the differential shell; a first friction mechanism mounted between the differential left end cap and the differential housing; a second friction mechanism mounted between the differential right end cap and the differential housing; the gear module of the left planetary gear and the gear module of the right planetary gear are 2.5-3.5; the number of teeth of the left planetary gear and the number of teeth of the right planetary gear are 6-8; the pressure angle between the left planetary gear and the right planetary gear is 20-30 degrees; the helical angle of the left planetary gear and the right planetary gear is 30-45 degrees; therefore, the structural parameters and the arrangement of the left planetary gear, the right planetary gear, the left half axle gear and the right half axle gear are reasonably set; when the vehicle is in working conditions such as slipping, torque difference exists between the two wheels due to different ground adhesion and is transmitted to the left and right axle gears, and the differential can automatically sense the differential according to the torque difference; the left planetary gear and the right planetary gear revolve around the axis of the half axle gear and simultaneously rotate around the axis of the left planetary gear and the right planetary gear, and the left planetary gear, the right planetary gear, the left half axle gear and the right half axle gear are meshed to generate axial force, so that a large friction torque is generated between the end faces of the gears; and axial force is transmitted to the first friction mechanism and the second friction mechanism, friction force generated between the friction mechanisms further limits the planetary gear to rotate, namely, internal friction torque is further generated, and the slip limiting capacity of the differential is improved.
Drawings
FIG. 1 is a schematic diagram of an overall structure of a limited slip differential according to an embodiment of the present invention;
FIG. 2 is a schematic diagram illustrating a partial structure of a limited slip differential according to an embodiment of the present invention;
FIG. 3 is a schematic structural diagram of a left planetary gear engaged with a right planetary gear according to an embodiment of the present invention;
FIG. 4 is a schematic structural diagram of a first friction mechanism according to an embodiment of the present invention;
FIG. 5 is a schematic structural diagram of a second friction mechanism according to an embodiment of the present invention;
FIG. 6 is a schematic view of a heat dissipation arrangement on a left end cover side of the differential according to an embodiment of the present invention;
FIG. 7 is a schematic view of a heat dissipation arrangement on the other side of the left end cover of the differential according to an embodiment of the present invention;
fig. 8 is a schematic structural view of a limited slip differential mounted on a vehicle body according to an embodiment of the present invention.
Detailed Description
In order to solve the technical problems that the antiskid differential mechanism in the prior art is complex in structure and cannot have insufficient limited slip capacity, the invention provides a main speed reducer of a limited slip differential mechanism assembly, which comprises: the spiral bevel gear is connected with a right end cover of the differential, the right end cover of the differential is connected with a differential shell, and the differential shell is also connected with a left end cover of the differential; a left planetary gear mounted in the differential left end cap; a right planetary gear mounted in the differential right end cap; a left side gear mounted in a first gear mounting hole at one end of the differential case; the right half shaft gear is installed in a second gear installation hole in the other end of the differential shell; a first friction mechanism mounted between the differential left end cap and the differential housing; a second friction mechanism mounted between the differential right end cap and the differential housing; the gear module of the left planetary gear and the gear module of the right planetary gear are 2.5-3.5; the number of teeth of the left planetary gear and the number of teeth of the right planetary gear are 6-8; the pressure angle between the left planetary gear and the right planetary gear is 20-30 degrees; the helical angle of the left planetary gear and the right planetary gear is 30-45 degrees.
The technical solution of the present invention is further described in detail by the accompanying drawings and the specific embodiments.
Example one
The present embodiment provides a limited slip differential assembly, as shown in fig. 1, comprising: the differential mechanism comprises a spiral bevel gear 1, a differential right end cover 2, a differential shell 3, a differential left end cover 4, a left planetary gear 5, a right planetary gear 6, a left half-axle gear 7, a right half-axle gear 8, a first friction mechanism 9 and a second friction mechanism 10; wherein,
spiral bevel gear 1 links to each other through first connecting bolt 11 with differential mechanism right-hand member lid 2, differential mechanism right-hand member lid 2 links to each other with differential mechanism casing 3 through second connecting bolt 12, differential mechanism is parallel helical gear formula differential mechanism, for example tusson differential mechanism.
The differential case 3 is also connected to the differential left end cover 4 by a third connecting bolt 13. The left planetary gears 5 are uniformly arranged in the differential left end cover 4; the right planetary gears 6 are uniformly arranged in the differential right end cover 2; the left side gear 7 is mounted in a first gear mounting hole at one end of the differential case 3, the right side gear 8 is mounted in a second gear mounting hole at the other end of the differential case 3, and the first friction mechanism 9 is mounted between the differential left end cover 4 and the differential case 3; the second friction mechanism 10 is mounted between the differential right end cover 2 and the differential case 3. Wherein, the left side gear 7 and the right side gear 8 are coaxial with the differential case 3.
Specifically, referring to fig. 2, the left planetary gear 5 and the right planetary gear 6 are mounted between the left side gear 7 and the right side gear 8, and the left planetary gear 5 includes: a first planetary gear 21, a second planetary gear 22, a third planetary gear 23, and a fourth planetary gear 24; the right planetary gear 6 includes: fifth, sixth, seventh and eighth planetary gears 31, 32, 33 and 34; wherein, referring to fig. 3, the first planetary gear 21, the second planetary gear 22, the third planetary gear 23 and the fourth planetary gear 24 are respectively mounted in corresponding left planetary gear mounting holes in the differential left end cover 4; the fifth planetary gear 31, the sixth planetary gear 32, the seventh planetary gear 33 and the eighth planetary gear 34 are respectively mounted in corresponding right planetary gear mounting holes in the differential right end cover 2.
Also, the first planetary gear 21 meshes with the fifth planetary gear 31; the second planetary gears 32 are meshed with the sixth planetary gears 32; the third planet gears 23 mesh with the seventh planet gears 33; the fourth planetary gears 24 mesh with the eighth planetary gears 34. The left side gear 7 meshes with the first planetary gear 21, the second planetary gear 22, the third planetary gear 23, and the fourth planetary gear 24, respectively; the right half shaft gear 8 meshes with the fifth planetary gear 31, the sixth planetary gear 32, the seventh planetary gear 33, and the eighth planetary gear 34, respectively.
Here, in order to meet the meshing requirement of the gear transmission, there is an offset angle between each left planetary gear mounting hole and each corresponding right planetary gear mounting hole, and the angle of the offset angle is determined according to the type of the planetary gear.
In addition, in order to meet the requirements of high torque (at least 14000N × m), high rotating speed (at least 4000r/min) and limited installation space of the off-road vehicle, various parameters of the left planetary gear and the right planetary gear need to be reasonably set, such as the gear module of the left planetary gear and the right planetary gear is 2.5-3.5, preferably 3; the number of teeth of the left planetary gear and the number of teeth of the right planetary gear are 6-8, and 6 is preferred; the pressure angle between the left planetary gear and the right planetary gear is 20-30 degrees, and preferably 30 degrees; the helical angle of the left planetary gear and the right planetary gear is 30-45 degrees, and preferably 37.5 degrees; the number of teeth of the left half shaft gear and the right half shaft gear is 18-20, preferably 18; the number of the left planet gears and the right planet gears is 4, the distribution positions are equal, and the like, so that under the slipping running working condition, proper axial force is generated through the autorotation of the left planet gears and the autorotation of the right planet gears, and accordingly, the end faces of the gears generate large friction torque, and the self slip limiting capacity of the differential can be effectively improved.
In order to further improve the internal friction torque of the differential assembly, a first friction mechanism 9 and a second friction mechanism 10 are further arranged; referring to fig. 4, the first friction mechanism 9 includes: a first lock ring 41, a first outer friction plate 42, a first outer friction plate 43, a first inner friction plate 44, a second outer friction plate 45, a second inner friction plate 46, a third outer friction plate 47, and a third inner friction plate 48; wherein,
the first locking ring 41 is slidably connected with the left side gear 7; the first outer friction plate 42, the first outer friction plate 43, the first inner friction plate 44, the second outer friction plate 45, the second inner friction plate 46, the third outer friction plate 47 and the third inner friction plate 48 are sequentially installed between the first lock ring and the differential case 3 in this order; the outer sides of the first outer friction disc 42, the first outer friction disc 43, the second outer friction disc 45 and the third outer friction disc 47 are all provided with tooth shapes, so that the first outer friction disc 42, the first outer friction disc 43, the second outer friction disc 45 and the third outer friction disc 47 are correspondingly installed in reserved tooth-shaped installation holes of the differential case 3; the involute splines of the first inner friction plate 44, the second inner friction plate 46 and the third inner friction plate 48 are all connected with the involute splines on the excircle of the first locking ring 41 in a matching way.
Likewise, referring to fig. 5, the second friction mechanism 10 includes: a second lock ring 51, a second outer friction disk 52, a fourth outer friction disk 53, a fourth inner friction disk 54, a fifth outer friction disk 55, a fifth inner friction disk 56, a sixth outer friction disk 57, and a sixth inner friction disk 58; wherein, the second locking ring 51 is connected with the right half shaft gear 8 in a sliding way; the second outer friction disk 52, the fourth outer friction disk 53, the fourth inner friction disk 54, the fifth outer friction disk 55, the fifth inner friction disk 56, the sixth outer friction disk 57 and the sixth inner friction disk 58 are sequentially mounted between the second lock ring and the differential case in this order;
the outer sides of the second outer friction disc 52, the fourth outer friction disc 53, the fifth outer friction disc 55 and the sixth outer friction disc 57 are all provided with a tooth pattern, so that the second outer friction disc 52, the fourth outer friction disc 53, the fifth outer friction disc 55 and the sixth outer friction disc 57 can be correspondingly installed in a tooth pattern installation hole reserved in the differential case 3; the involute splines of the fourth inner friction plate 54, the fifth inner friction plate 56 and the sixth inner friction plate 58 are connected with the involute splines on the excircle of the second locking ring 51 in a matched manner.
In addition, if the differential mechanism works under the differential operating mode, the mutual friction between the friction plates of the first friction mechanism 9 and the second friction mechanism 10 can enable the differential mechanism to generate a large amount of heat, in order to dissipate heat in time, the differential mechanism left end cover 4 and the differential mechanism right end cover 2 are respectively provided with an oil collecting pool and oil holes for lubricating and dissipating heat, the differential mechanism left end cover 4 is taken as an example, see fig. 6, one side of the differential mechanism left end cover 4 is provided with the oil collecting pool 61, so that more lubricating oil can be stored at the heat source of the first friction mechanism 9, the oil collecting pool 61 can be used for taking away and circulating the heat, and the first friction mechanism 9 can be effectively lubricated and dissipated heat.
Referring to fig. 7, an oil sump 62 is disposed on the differential case 3, oil passing holes 63 are uniformly disposed on the differential case 3, the number of the oil passing holes 63 can be set according to actual needs, and in this embodiment, the number of the oil passing holes 63 includes 4. The oil through hole 63 is mainly used to circulate lubricating oil inside the differential case 3, and is used to lubricate and dissipate heat from the left planetary gear 5 and the left side gear 7.
Further, an oil passing hole 64 is formed in the matching position of the excircle of the left end cover 4 of the differential and the left planetary gear 5, and the oil passing hole 64 can fully lubricate and dissipate heat of the left planetary gear under the differential working condition. Therefore, a circulating closed loop is formed in a limited space through the fine design and arrangement of the oil collecting pool 61, the oil collecting pool 62, the oil passing hole 62 and the oil passing hole 63, all parts of the differential can be sufficiently lubricated and radiated, and the reliability of the differential is greatly improved.
In practical application, power is input by the spiral bevel gear 1, and is transmitted to the left half axle gear 7 and the right half axle gear 8 through the differential right end cover 2, the differential shell 3, the left planetary gear 5 and the right planetary gear 6 respectively, the left half axle gear 7 transmits the power to the left half axle shaft, and the right half axle gear 8 transmits the power to the right wheel-side half axle. Under the condition that the left wheel and the right wheel are not differential, power is evenly distributed to the left half shaft gear and the right half shaft gear through the differential shell 3 and the left planetary gear and the right planetary gear respectively, and the left planetary gear and the right planetary gear only revolve around an axis at the moment; if the left wheel and the right wheel have differential speed, the left planetary gear and the right planetary gear not only revolve around the axis, but also rotate around the self axis, wherein the rotating directions of the left planetary gear and the right planetary gear are opposite, so that the differential speed of the left axle gear and the right axle gear can be realized.
Example two
In accordance with a first embodiment, the present embodiment further provides a final drive including the differential assembly of the first embodiment, the final drive being mounted on a chassis of a heavy off-road vehicle, and specifically, referring to fig. 8, the vehicle body chassis being provided with a differential mounting support 81; a first conical roller bearing 83 and a second conical roller bearing 84 are respectively mounted at two ends of the differential assembly 82, and the differential assembly 82 is mounted in the differential mounting support 81 through the first conical roller bearing 83 and the second conical roller bearing 84; the differential mounting support 81 is connected with a reducer housing 83; the differential assembly 82 is connected with a left wheel side half shaft 85 and a right wheel side half shaft 86 through involute splines respectively.
In the working process, power is input by the spiral bevel gear 1, and is transmitted to the left half axle gear 7 and the right half axle gear 8 through the differential right end cover 2, the differential shell 3, the left planetary gear 5 and the right planetary gear 6 respectively, the left half axle gear 7 transmits the power to the left half axle 83, and the right half axle gear 8 transmits the power to the right wheel-side half axle 84. Under the condition that the left wheel and the right wheel are not differential, power is evenly distributed to the left half shaft gear and the right half shaft gear through the differential shell 3 and the left planetary gear and the right planetary gear respectively, and the left planetary gear and the right planetary gear only revolve around an axis at the moment; if the left wheel and the right wheel have differential speed, the left planetary gear and the right planetary gear not only revolve around the axis, but also rotate around the self axis, wherein the rotating directions of the left planetary gear and the right planetary gear are opposite, so that the differential speed of the left axle gear and the right axle gear can be realized.
Specifically, as shown in fig. 1, the differential assembly includes: the differential mechanism comprises a spiral bevel gear 1, a differential right end cover 2, a differential shell 3, a differential left end cover 4, a left planetary gear 5, a right planetary gear 6, a left half-axle gear 7, a right half-axle gear 8, a first friction mechanism 9 and a second friction mechanism 10; wherein,
spiral bevel gear 1 links to each other through first connecting bolt 11 with differential mechanism right-hand member lid 2, differential mechanism right-hand member lid 2 links to each other with differential mechanism casing 3 through second connecting bolt 12, differential mechanism is parallel helical gear formula differential mechanism, for example tusson differential mechanism.
The differential case 3 is also connected to the differential left end cover 4 by a third connecting bolt 13. The left planetary gears 5 are uniformly arranged in the differential left end cover 4; the right planetary gears 6 are uniformly arranged in the differential right end cover 2; the left side gear 7 is mounted in a first gear mounting hole at one end of the differential case 3, the right side gear 8 is mounted in a second gear mounting hole at the other end of the differential case 3, and the first friction mechanism 9 is mounted between the differential left end cover 4 and the differential case 3; the second friction mechanism 10 is mounted between the differential right end cover 2 and the differential case 3. Wherein, the left side gear 7 and the right side gear 8 are coaxial with the differential case 3.
Specifically, referring to fig. 2, the left planetary gear 5 and the right planetary gear 6 are mounted between the left side gear 7 and the right side gear 8, and the left planetary gear 5 includes: a first planetary gear 21, a second planetary gear 22, a third planetary gear 23, and a fourth planetary gear 24; the right planetary gear 6 includes: fifth, sixth, seventh and eighth planetary gears 31, 32, 33 and 34; wherein, referring to fig. 3, the first planetary gear 21, the second planetary gear 22, the third planetary gear 23 and the fourth planetary gear 24 are respectively mounted in corresponding left planetary gear mounting holes in the differential left end cover 4; the fifth planetary gear 31, the sixth planetary gear 32, the seventh planetary gear 33 and the eighth planetary gear 34 are respectively mounted in corresponding right planetary gear mounting holes in the differential right end cover 2.
Also, the first planetary gear 21 meshes with the fifth planetary gear 31; the second planetary gears 32 are meshed with the sixth planetary gears 32; the third planet gears 23 mesh with the seventh planet gears 33; the fourth planetary gears 24 mesh with the eighth planetary gears 34. The left side gear 7 meshes with the first planetary gear 21, the second planetary gear 22, the third planetary gear 23, and the fourth planetary gear 24, respectively; the right half shaft gear 8 meshes with the fifth planetary gear 31, the sixth planetary gear 32, the seventh planetary gear 33, and the eighth planetary gear 34, respectively.
Here, in order to meet the meshing requirement of the gear transmission, there is an offset angle between each left planetary gear mounting hole and each corresponding right planetary gear mounting hole, and the angle of the offset angle is determined according to the type of the planetary gear.
In addition, in order to meet the requirements of high torque (at least 14000N × m), high rotation speed (at least 4000r/min) and limited installation space of the off-road vehicle, various parameters of the left planetary gear and the right planetary gear need to be reasonably set, such as the gear module of the left planetary gear and the right planetary gear is 2.5-3.5, preferably 3; the number of teeth of the left planetary gear and the number of teeth of the right planetary gear are 6-8, and 6 is preferred; the pressure angle between the left planetary gear and the right planetary gear is 20-30 degrees, and preferably 30 degrees; the helical angle of the left planetary gear and the right planetary gear is 30-45 degrees, and preferably 37.5 degrees; the number of teeth of the left half shaft gear and the right half shaft gear is 18-20, preferably 18; the number of the left planet gears and the right planet gears is 4, the distribution positions are equal, and the like, so that under the slipping running working condition, proper axial force is generated through the autorotation of the left planet gears and the autorotation of the right planet gears, and accordingly, the end faces of the gears generate large friction torque, and the self slip limiting capacity of the differential can be effectively improved.
In order to further improve the internal friction torque of the differential assembly, a first friction mechanism 9 and a second friction mechanism 10 are further arranged; referring to fig. 4, the first friction mechanism 9 includes: a first lock ring 41, a first outer friction plate 42, a first outer friction plate 43, a first inner friction plate 44, a second outer friction plate 45, a second inner friction plate 46, a third outer friction plate 47, and a third inner friction plate 48; wherein,
the first locking ring 41 is slidably connected with the left side gear 7; the first outer friction plate 42, the first outer friction plate 43, the first inner friction plate 44, the second outer friction plate 45, the second inner friction plate 46, the third outer friction plate 47 and the third inner friction plate 48 are sequentially installed between the first lock ring and the differential case 3 in this order; the outer sides of the first outer friction disc 42, the first outer friction disc 43, the second outer friction disc 45 and the third outer friction disc 47 are all provided with tooth shapes, so that the first outer friction disc 42, the first outer friction disc 43, the second outer friction disc 45 and the third outer friction disc 47 are correspondingly installed in reserved tooth-shaped installation holes of the differential case 3; the involute splines of the first inner friction plate 44, the second inner friction plate 46 and the third inner friction plate 48 are all connected with the involute splines on the excircle of the first locking ring 41 in a matching way.
Likewise, referring to fig. 5, the second friction mechanism 10 includes: a second lock ring 51, a second outer friction disk 52, a fourth outer friction disk 53, a fourth inner friction disk 54, a fifth outer friction disk 55, a fifth inner friction disk 56, a sixth outer friction disk 57, and a sixth inner friction disk 58; wherein, the second locking ring 51 is connected with the right half shaft gear 8 in a sliding way; the second outer friction disk 52, the fourth outer friction disk 53, the fourth inner friction disk 54, the fifth outer friction disk 55, the fifth inner friction disk 56, the sixth outer friction disk 57 and the sixth inner friction disk 58 are sequentially mounted between the second lock ring and the differential case in this order;
the outer sides of the second outer friction disc 52, the fourth outer friction disc 53, the fifth outer friction disc 55 and the sixth outer friction disc 57 are all provided with a tooth pattern, so that the second outer friction disc 52, the fourth outer friction disc 53, the fifth outer friction disc 55 and the sixth outer friction disc 57 can be correspondingly installed in a tooth pattern installation hole reserved in the differential case 3; the involute splines of the fourth inner friction plate 54, the fifth inner friction plate 56 and the sixth inner friction plate 58 are connected with the involute splines on the excircle of the second locking ring 51 in a matched manner.
In addition, if the differential mechanism works under the differential operating mode, the mutual friction between the friction plates of the first friction mechanism 9 and the second friction mechanism 10 can enable the differential mechanism to generate a large amount of heat, in order to dissipate heat in time, the differential mechanism left end cover 4 and the differential mechanism right end cover 2 are respectively provided with an oil collecting pool and oil holes for lubricating and dissipating heat, the differential mechanism left end cover 4 is taken as an example, see fig. 6, one side of the differential mechanism left end cover 4 is provided with the oil collecting pool 61, so that more lubricating oil can be stored at the heat source of the first friction mechanism 9, the oil collecting pool 61 can be used for taking away and circulating the heat, and the first friction mechanism 9 can be effectively lubricated and dissipated heat.
Referring to fig. 7, an oil sump 62 is disposed on the differential case 3, oil passing holes 63 are uniformly disposed on the differential case 3, the number of the oil passing holes 63 can be set according to actual needs, and in this embodiment, the number of the oil passing holes 63 includes 4. The oil through hole 63 is mainly used to circulate lubricating oil inside the differential case 3, and is used to lubricate and dissipate heat from the left planetary gear 5 and the left side gear 7.
Further, an oil passing hole 64 is formed in the matching position of the excircle of the left end cover 4 of the differential and the left planetary gear 5, and the oil passing hole 64 can fully lubricate and dissipate heat of the left planetary gear under the differential working condition. Therefore, a circulating closed loop is formed in a limited space through the fine design and arrangement of the oil collecting pool 61, the oil collecting pool 62, the oil passing hole 62 and the oil passing hole 63, all parts of the differential can be sufficiently lubricated and radiated, and the reliability of the differential is greatly improved.
The embodiment of the invention provides a limited slip differential assembly and a main speed reducer, which have the following beneficial effects that:
the invention provides a limited slip differential assembly and a main speed reducer, wherein the differential assembly comprises: the spiral bevel gear is connected with a right end cover of the differential, the right end cover of the differential is connected with a differential shell, and the differential shell is also connected with a left end cover of the differential; a left planetary gear mounted in the differential left end cap; a right planetary gear mounted in the differential right end cap; a left side gear mounted in a first gear mounting hole at one end of the differential case; the right half shaft gear is installed in a second gear installation hole in the other end of the differential shell; a first friction mechanism mounted between the differential left end cap and the differential housing; a second friction mechanism mounted between the differential right end cap and the differential housing; the gear module of the left planetary gear and the gear module of the right planetary gear are 2.5-3.5; the number of teeth of the left planetary gear and the number of teeth of the right planetary gear are 6-8; the pressure angle between the left planetary gear and the right planetary gear is 20-30 degrees; the helical angle of the left planetary gear and the right planetary gear is 30-45 degrees; therefore, the structural parameters and the arrangement of the left planetary gear, the right planetary gear, the left half axle gear and the right half axle gear are reasonably set; when the vehicle is in working conditions such as slipping, torque difference exists between the two wheels due to different ground adhesion and is transmitted to the left and right axle gears, and the differential can automatically sense the differential according to the torque difference; the left planetary gear and the right planetary gear revolve around the axis of the half axle gear and simultaneously rotate around the axis of the left planetary gear and the right planetary gear, and the left planetary gear, the right planetary gear, the left half axle gear and the right half axle gear are meshed to generate axial force, so that a large friction torque is generated between the end faces of the gears; and axial force is transmitted to the first friction mechanism and the second friction mechanism, friction force generated between the friction mechanisms further limits the planetary gear to rotate, namely, internal friction torque is further generated, and the slip limiting capacity of the torque induction type automatic slip limiting differential is improved.
The above description is only exemplary of the present invention and should not be taken as limiting the scope of the present invention, and any modifications, equivalents, improvements, etc. that are within the spirit and principle of the present invention should be included in the present invention.
Claims (10)
1. A limited slip differential assembly, comprising:
the spiral bevel gear is connected with a right end cover of the differential, the right end cover of the differential is connected with a differential shell, and the differential shell is also connected with a left end cover of the differential;
a left planetary gear mounted in the differential left end cap;
a right planetary gear mounted in the differential right end cap;
a left side gear mounted in a first gear mounting hole at one end of the differential case;
the right half shaft gear is installed in a second gear installation hole in the other end of the differential shell;
a first friction mechanism mounted between the differential left end cap and the differential housing;
a second friction mechanism mounted between the differential right end cap and the differential housing; wherein,
the gear module of the left planetary gear and the gear module of the right planetary gear are 2.5-3.5; the number of teeth of the left planetary gear and the number of teeth of the right planetary gear are 6-8; the pressure angle between the left planetary gear and the right planetary gear is 20-30 degrees; the helical angle of the left planetary gear and the right planetary gear is 30-45 degrees.
2. A differential assembly as claimed in claim 1, wherein said left planetary gear comprises: a first planetary gear, a second planetary gear, a third planetary gear and a fourth planetary gear; the right planetary gear includes: a fifth planetary gear, a sixth planetary gear, a seventh planetary gear and an eighth planetary gear; wherein,
the first planetary gear, the second planetary gear, the third planetary gear and the fourth planetary gear are respectively installed in corresponding planetary gear installation holes in a left end cover of the differential mechanism;
the fifth planetary gear, the sixth planetary gear, the seventh planetary gear and the eighth planetary gear are respectively installed in corresponding planetary gear installation holes in the right end cover of the differential.
3. A differential assembly as claimed in claim 2, wherein said first planetary gear is in mesh with said fifth planetary gear; the second planetary gear is meshed with the sixth planetary gear; the third planetary gear is meshed with the seventh planetary gear; the fourth planetary gear is meshed with the eighth planetary gear;
the left side gear is meshed with the first planetary gear, the second planetary gear, the third planetary gear and the fourth planetary gear respectively;
the right half shaft gear is respectively meshed with the fifth planetary gear, the sixth planetary gear, the seventh planetary gear and the eighth planetary gear.
4. A differential assembly as recited in claim 1, wherein said first friction mechanism comprises: the friction plate comprises a first locking ring, a first outer friction plate, a first inner friction plate, a second outer friction plate, a second inner friction plate, a third outer friction plate and a third inner friction plate; wherein,
the first locking ring is connected with the left half shaft gear in a sliding mode;
the first outer friction disc, the first inner friction disc, the second outer friction disc, the second inner friction disc, the third outer friction disc and the third inner friction disc are sequentially arranged between the first locking ring and the differential shell in sequence;
the first outer friction disc, the second outer friction disc and the third outer friction disc are correspondingly installed in tooth-shaped installation holes reserved in the differential shell;
the involute splines of the first inner friction plate, the second inner friction plate and the third inner friction plate are matched and connected with the involute splines on the excircle of the first locking ring.
5. A differential assembly as recited in claim 1, wherein said second friction mechanism comprises: a second lock ring, a second outer friction disk, a fourth inner friction disk, a fifth outer friction disk, a fifth inner friction disk, a sixth outer friction disk and a sixth inner friction disk; wherein,
the second locking ring is connected with the right half shaft gear in a sliding manner;
the second outer friction disc, the fourth inner friction disc, the fifth outer friction disc, the fifth inner friction disc, the sixth outer friction disc and the sixth inner friction disc are sequentially arranged between the second lock ring and the differential shell in sequence;
the second outer friction disc, the fourth outer friction disc, the fifth outer friction disc and the sixth outer friction disc are correspondingly installed in tooth-shaped installation holes reserved in the differential shell;
the involute splines of the fourth inner friction plate, the fifth inner friction plate and the sixth inner friction plate are matched and connected with the involute splines on the excircle of the second locking ring.
6. A differential assembly as claimed in claim 1, wherein said differential left end cover and said differential right end cover are provided with oil lubrication holes and oil sumps.
7. A differential assembly as claimed in claim 1, wherein said differential is a parallel helical gear differential.
8. A differential assembly as claimed in claim 1, wherein said left side gear, said right side gear and said differential case are coaxial.
9. A differential assembly as recited in claim 2, wherein there is an offset angle between said left planet gear mounting aperture and said right planet gear mounting aperture.
10. A final drive, characterized in that it comprises a differential assembly according to any one of claims 1 to 9.
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| CN201710456603.6A CN107387714B (en) | 2017-06-16 | 2017-06-16 | A kind of limited-slip differential assembly and main reducing gear |
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| CN113958681A (en) * | 2021-09-28 | 2022-01-21 | 东风汽车零部件(集团)有限公司刃量具分公司 | Large helical angle gear type limited slip differential |
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| CN107387714B (en) | 2019-08-13 |
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