CN103047387A - Cylindrical gear power-shunted limited slip differential - Google Patents
Cylindrical gear power-shunted limited slip differential Download PDFInfo
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- CN103047387A CN103047387A CN 201310010192 CN201310010192A CN103047387A CN 103047387 A CN103047387 A CN 103047387A CN 201310010192 CN201310010192 CN 201310010192 CN 201310010192 A CN201310010192 A CN 201310010192A CN 103047387 A CN103047387 A CN 103047387A
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- gear set
- sun gear
- planetary gear
- slip differential
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Abstract
The invention provides a cylindrical gear power-shunted limited slip differential which comprises a first shell, a second shell, and a first sun gear and a second sun gear which are arranged on a same spindle; a first planet gear set is evenly arranged on the circumference of the first sun gear, and a second planet gear set is evenly arranged on the circumference of the second sun gear, and the planet gears of the first planet gear set and the planet gears of the second planet gear set are arranged at mutual intervals; each planet gear of the first gear set engages with two neighboring planet gears of the second planet gear set, and each planet gear of the second gear set engages with two neighboring planet gears of the first planet gear set. The cylindrical gear power-shunted limited slip differential has the advantages that power shunting function is achieved through the stagger engagement between the first planet gear set and the second planet gear set; stress of gear teeth is reduced; abrasion between inner cavities of the shells and the planet gears are reduced; and the service life of the differential is elongated.
Description
Technical field
The invention belongs to a kind of mechanical transmission box of tricks, especially relate to the limited-slip differential that a kind of power can be shunted.
Background technique
Differential mechanism is mainly used in the transmission system of automobile, and when there was speed discrepancy in left and right sidesing driving wheel, differential mechanism was distributed to the torque of slow-speed driving wheel greater than the torque that turns soon driving wheel.The planetary pinion of tradition cylinder screw gear type limited-slip differential is during with the planetary pinion engagement, and main passive planetary pinion is 1, because not shunting of power, so that gear tooth stresses is large during engagement, and the life-span weak point.
Summary of the invention
The problem to be solved in the present invention provides the staggered engagement of a kind of planetary pinion, and is stressed even, reaches the effect of dynamic branch, prolongs the limited-slip differential in planetary pinion life-span.
For solving the problems of the technologies described above, technological scheme of the present invention is:
A kind of cylindrical gears dynamic branch formula limited-slip differential, comprise the first housing and the second housing, described the first enclosure interior is provided with the first sun gear, described the second enclosure interior is provided with the second sun gear, described the first sun gear and the coaxial setting of described the second sun gear, described the first sun gear periphery evenly is provided with the first planetary gear set that is meshed with the first sun gear, described the second sun gear periphery evenly is provided with the second planetary gear set that is meshed with the second sun gear, the planetary pinion interval of described the first planetary gear set and described the second planetary gear set arranges, and two adjacent in the arbitrary planetary pinion in described the first planetary gear set and described the second planetary gear set planetary pinions are meshed, and two adjacent in the arbitrary planetary pinion in described the second planetary gear set and described the first planetary gear set planetary pinions are meshed.
Included 4-6 planetary pinion in described the first planetary gear set and described the second planetary gear set.
5 planetary pinions have been included in described the first planetary gear set and described the second planetary gear set.
Be provided with the planetary pinion setting sleeve between each planetary pinion in described the first sun gear and described the first planetary gear set, be provided with the planetary pinion setting sleeve between each planetary pinion in described the second sun gear and described the second planetary gear set, be equipped with thrust block in the described planetary pinion setting sleeve.
Described thrust block contains 2 taper cushions and 3 plane pads.
Described the second housing is provided with the mileage gauge stand.
Advantage and good effect that the present invention has are: owing to adopt technique scheme, each planetary pinion in the first planetary gear set and the second planetary gear set has two planetary pinions that match to be meshed, so that any planetary pinion is stressed evenly, realize the even of transmission of power, so just reduced the planetary pinion gear tooth stresses, also reduce housing inner chamber and planetary wearing and tearing, improved the life-span of limited-slip differential assembly.
Description of drawings
Fig. 1 is assembling schematic representation of the present invention
Fig. 2 is sectional view of the present invention
Fig. 3 is the present invention's the first sun gear, the first planetary gear set, the second planetary gear set and the second sun gear meshing relation schematic perspective view
Among the figure:
1, the first housing 2, the first planetary gear set 3, the second housing
4, mileage gauge stand 5, the second sun gear 6, the second planetary gear set
7, planetary pinion setting sleeve 8, thrust block 9, plane pad
10, taper cushion 11, the first sun gear
Embodiment
As Figure 1-3, cylindrical gears dynamic branch formula limited-slip differential of the present invention, comprise the first housing 1 and the second housing 3, described the first housing 1 inside is provided with the first sun gear 11, described the second housing 3 inside are provided with the second sun gear 5, described the first sun gear 11 and the 5 coaxial settings of described the second sun gear, described the first sun gear 11 peripheries evenly are provided with the first planetary gear set 2 that is meshed with the first sun gear 11, described the second sun gear 5 peripheries evenly are provided with the second planetary gear set 6 that is meshed with the second sun gear 5, described the first planetary gear set 2 arranges with the planetary pinion interval of described the second planetary gear set 6, and two adjacent in the arbitrary planetary pinion in described the first planetary gear set 2 and described the second planetary gear set 6 planetary pinions are meshed, and two adjacent in the arbitrary planetary pinion in described the second planetary gear set 6 and described the first planetary gear set 2 planetary pinions are meshed.
Included 4-6 planetary pinion in described the first planetary gear set 2 and described the second planetary gear set 6.
In the present embodiment, 5 planetary pinions have been included in the first planetary gear set 2 and the second planetary gear set 6.
Be provided with planetary pinion setting sleeve 7 between each planetary pinion in described the first sun gear 5 and described the first planetary gear set 2, be provided with planetary pinion setting sleeve 7 between each planetary pinion in described the second sun gear 5 and described the second planetary gear set 6, be equipped with thrust block 8 in the described planetary pinion setting sleeve 7.Be mated by spline joint by 2 thrust blocks 8 in the described planetary pinion setting sleeve 7 and install and use, two thrust blocks 8 include 2 taper cushions 10 and 3 plane pads 9, be mainly used in adjusting axial clearance, sun gear and planetary pinion are better meshed, obtain preferably meshing zone.
In the present embodiment, the second housing 3 is provided with mileage gauge stand 4.
Described planetary pinion adopts the Double drum type toothing.Crowned teeth is higher than the bearing capacity of straight-tooth, and contact precision will be got well.Simultaneously, because drum-shaped tooth improves the contact conditions of gear, avoided the drawback that the extruding of straight-tooth increment seamed edge, stress are concentrated in the transmitting torque process.Improve gear tooth friction, wear condition, reduced noise.Transmission efficiency also increases.
Planetary pinion can be quaternion or six one group, needn't be five one group, and the number that planetary pinion is every group is according to the product space design and sun gear is big or small decides.
When normally travelling: automobile rotational speed passes to the differential mechanism gear ring via motor, clutch, speed changer, and the differential mechanism gear ring links to each other with differential casing (the first housing 1, the second housing 3).When normally travelling, about two vehicle wheel rotational speeds identical, 5 planetary pinions that the rotation of housing assembly drives the first planetary gear set 2 rotate jointly, the planetary external tooth of the first planetary gear set 2 is stirred the first sun gear 11 and is rotated, this moment, the planetary pinion gear teeth were equivalent to key, there is no engagement between it and the sun gear, only simple revolution is transmitted and is rotated.Be positioned at equally 5 planetary pinion revolution of endoceliac the second planetary gear set 6 of shell, the planetary gear teeth of the second planetary gear set 6 are stirred the second sun gear 5 and are rotated.Whole differential mechanism keeps certain rotating speed, and all gears in housing and the internal structure are without relative movement.At this moment, the axial force that housing produces when bearing each cylindrical screw gear transmission motion is in impaction state, but does not mutually have friction torque.
Two wheels meet that adhesion does not wait or when differing larger the road surface and skidding such as a side: about have speed discrepancy between two wheels, sun gear is relative with planetary pinion to produce engagement, because the effect of speed discrepancy and axial force produces friction torque between housing and the planetary pinion.At the fast end of rotating speed, the direction of the friction torque of generation and driving moment opposite direction so driving moment is little, reduce its rotating speed; At the slow end of rotating speed, friction torque is identical with the direction of driving moment, and driving moment is large, makes it increase to enough towing motorcars and rolls the obstacle road surface away from.Like this, differential mechanism has just been finished the work of regulating voluntarily, distributing driving moment.Simultaneously owing to 2 adjacent with its (single planetary pinion) in any single planetary pinion in the first planetary gear set 2 or the second planetary gear set 6 and another group planetary pinions are intermeshing, so that its (single planetary pinion) power evenly passes to 2 other one group planetary pinions, that is to say and reduced the planetary pinion gear tooth stresses, improved the planetary life-span.
As shown in Figure 3, this limited-slip differential internal structure is compact, and parts are more, and each gear can produce enough axial forces and friction torque when all having larger helix angle to have speed discrepancy with assurance.The design space of differential mechanism is subjected in many ways that factor restricts, and axial length is about 180mm, the about 168mm of outside diameter, and designing and developing dynamic branch formula limited-slip differential has certain difficulty.After designing and calculating repeatedly, former differential casing is divided into two, and is connected by seam; The cylindrical of sun gear cooperates with hole in the enclosure interior; Housing cooperates with planetary pinion, and play positioning action with the planetary pinion setting sleeve jointly; The input torque of automobile is 186Nm, this conditional decision sun gear and planetary intensity, also just determined its modulus, transverse tooth thickness etc.
More than one embodiment of the present of invention are had been described in detail, but described content only is preferred embodiments of the present invention, can not think only to be defined in practical range of the present invention.All equalizations of doing according to the present patent application scope change and improve etc., all should still belong within the patent covering scope of the present invention.
Claims (6)
1. cylindrical gears dynamic branch formula limited-slip differential, comprise the first housing and the second housing, described the first enclosure interior is provided with the first sun gear, described the second enclosure interior is provided with the second sun gear, described the first sun gear and the coaxial setting of described the second sun gear, it is characterized in that, described the first sun gear periphery evenly is provided with the first planetary gear set that is meshed with described the first sun gear, described the second sun gear periphery evenly is provided with the second planetary gear set that is meshed with described the second sun gear, the planetary pinion interval of described the first planetary gear set and described the second planetary gear set arranges, and two adjacent in the arbitrary planetary pinion in described the first planetary gear set and described the second planetary gear set planetary pinions are meshed, and two adjacent in the arbitrary planetary pinion in described the second planetary gear set and described the first planetary gear set planetary pinions are meshed.
2. cylindrical gears dynamic branch formula limited-slip differential according to claim 1 is characterized in that: included 4-6 planetary pinion in described the first planetary gear set and described the second planetary gear set.
3. cylindrical gears dynamic branch formula limited-slip differential according to claim 2 is characterized in that: included 5 planetary pinions in described the first planetary gear set and described the second planetary gear set.
4. cylindrical gears dynamic branch formula limited-slip differential according to claim 3, it is characterized in that: be provided with the planetary pinion setting sleeve between each planetary pinion in described the first sun gear and described the first planetary gear set, be provided with the planetary pinion setting sleeve between each planetary pinion in described the second sun gear and described the second planetary gear set, be equipped with thrust block in the described planetary pinion setting sleeve.
5. cylindrical gears dynamic branch formula limited-slip differential according to claim 4, it is characterized in that: described thrust block contains 2 taper cushions and 3 plane pads.
6. cylindrical gears dynamic branch formula limited-slip differential according to claim 1, it is characterized in that: described the second housing is provided with the mileage gauge stand.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201310010192 CN103047387A (en) | 2013-01-09 | 2013-01-09 | Cylindrical gear power-shunted limited slip differential |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201310010192 CN103047387A (en) | 2013-01-09 | 2013-01-09 | Cylindrical gear power-shunted limited slip differential |
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| Publication Number | Publication Date |
|---|---|
| CN103047387A true CN103047387A (en) | 2013-04-17 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN 201310010192 Pending CN103047387A (en) | 2013-01-09 | 2013-01-09 | Cylindrical gear power-shunted limited slip differential |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108240449A (en) * | 2016-12-27 | 2018-07-03 | 比亚迪股份有限公司 | Differential mechanism and vehicle |
-
2013
- 2013-01-09 CN CN 201310010192 patent/CN103047387A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108240449A (en) * | 2016-12-27 | 2018-07-03 | 比亚迪股份有限公司 | Differential mechanism and vehicle |
| CN108240449B (en) * | 2016-12-27 | 2019-12-20 | 比亚迪股份有限公司 | Differential and vehicle |
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Application publication date: 20130417 |