CN101886695A - Slip-limiting differential mechanism with noncircular bevel gear - Google Patents
Slip-limiting differential mechanism with noncircular bevel gear Download PDFInfo
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- CN101886695A CN101886695A CN 201010249465 CN201010249465A CN101886695A CN 101886695 A CN101886695 A CN 101886695A CN 201010249465 CN201010249465 CN 201010249465 CN 201010249465 A CN201010249465 A CN 201010249465A CN 101886695 A CN101886695 A CN 101886695A
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- differential mechanism
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Abstract
The invention relates to a slip-limiting differential mechanism with a noncircular bevel gear. The slip-limiting differential mechanism with the noncircular bevel gear consists of a differential mechanism shell, a noncircular planet gear and a noncircular half axle gear. The planet gear is connected with the shell by a shaft handle or a linear shaft and rotates with respect to the shell. The gear ratio of the noncircular planet gear to the noncircular half axle gear is 1: 2. The planet gear and the half axle gear adopt the noncircular bevel gear structures, the transmission ratio in an engagement process is not a fixed value, the change law of the transmission ratio is not limited by the number of the teeth, and the change range of the numerical value can be greatly improved. Therefore, the locking coefficient of the differential mechanism is improved, the pulsation and the impact are reduced simultaneously, and the cross-country requirements of cars are met. The invention is particularly suitable for various wheeled engineering machines of cross-country cars, dump trucks, wheel loaders, bulldozers and the like.
Description
Technical field
The invention belongs to mechanical engineering field, be specifically related to a kind of vehicle slip-limiting differential mechanism with noncircular bevel gear.
Background technique
Offroad vehicle will travel through the mire of being everlasting, soft surface even cross-country locality, and passing ability is one of its most important performance index.Differential mechanism is as the vitals of automobile, and its effect is a distribution of torque between two output shafts, and guarantees that two output shafts might rotate with different angular velocity, and its form and performance are directly connected to the passing ability of car load.
At present, China's offroad vehicle ransaxle also generally adopts symmetrical cone gear differential mechanism, and its two-semiaxle gear size is identical, can be with the torque left and right driving wheel of distributing on a rough average.When automobile travels on good road, such distribution for straight-line travelling still be turning driving all be satisfied.But when single wheel is in the very little smooth ground of coefficient of attachment,, also can't bring into play potential tractive force, cause automobile to travel although there is good adhering on opposite side wheel and ground.
The approach that addresses the above problem is to adopt the anti-slip differential device, increases locking coefficient.Common method mainly contains:
Adopt differential lock: when a wheel is in the less road surface of adhesion, can handle differential lock differential carrier and semiaxis are locked together, make differential mechanism not play differential action, this moment, locking coefficient was ∞, can make full use of left and right adhesion of taking turns like this, make tractive force reach possible maximum value.Before sailing the highway section that is difficult to walk in the automobile running into, can handle differential lock differential mechanism is pinned, cross the highway section that is difficult to walk after, should in time differential lock be unclamped, with the adverse consequences of avoiding occurring bringing because of the indifferential effect.
The friction type differential mechanism: its principle is to utilize the internal friction of mechanical component in the differential mechanism to increase locking coefficient.This differential design complexity, the requirement on machining accuracy height, easy to wear.Because need the ransaxle body structure is done bigger change, so generally can't install on the vehicle of having finalized the design, its Applicable scope is restricted.
The free wheel type differential mechanism: the free wheel type differential mechanism carries out work according to the speed discrepancy of left and right wheels, makes left and right sides semiaxis moment of torsion not have influence mutually.When single wheel skidded, it can automatically separate the semiaxis that changes driving wheel soon with differential mechanism, allow fast runner freely rotate, and all torsion torque is all passed to the slow-speed driving wheel.Shortcoming is a complex structure, and wearing and tearing and impulse ratio are more serious.
The gear ratio differential mechanism: differential bevel wheel is secondary if adopt variable ratio, then can rely on the barrier effect of variable ratio transmission to increase its locking coefficient under the prerequisite that does not change the ransaxle general structure, improves the cross-country passing ability of vehicle.But there are two big weakness in the gear ratio differential mechanism at present: the one, and the excursion of velocity ratio is too little, is not enough to overcome the influence of skidding; The 2nd, the period of change of velocity ratio is too short, easily produces pulsation and impacts.Its reason is that the velocity ratio of existing gear ratio differential mechanism is is a period of change with one of gear or three circular pitches, and its cycle is too short, and amplitude of variation is too little.
Summary of the invention
The purpose of this invention is to provide a kind of higher locking coefficient that has, can improve the limited slip differential of the cross-country passing capacity of vehicle.
Its technical solution of slip-limiting differential mechanism with noncircular bevel gear of the present invention is: it is made up of differential carrier, non-circular planetary gear, non-round differential gear, planetary pinion links and rotates to it by footstalk or a word axle and housing, non-circular planetary gear and non-round differential gear gear ratio are 1: 2, and non-circular planetary gear and non-round differential gear adopt non-cone gear structure.
Velocity ratio rule between non-circular planetary gear and the non-round differential gear is will put in order circle according to the corner of non-circular planetary gear to be arranged to 1 period of change.
Velocity ratio rule between non-circular planetary gear and the non-round differential gear is pressed following formula
Set, wherein: i
32Be differential gear and planetary velocity ratio, z
2, z
3Be respectively the planetary pinion and the differential gear number of teeth,
Be the planetary pinion corner, c=0～0.5 is a constant.
Planetary pinion of the present invention and differential gear adopt non-cone gear structure, velocity ratio no longer is a definite value in the engagement process, but change according to the rule of setting, planetary pinion turns around, and velocity ratio changes one-period, planetary pinion and differential gear gear ratio are 1: 2, the velocity ratio Changing Pattern is not limited by the number of teeth, can improve its numerical value change scope greatly, thereby improves the locking coefficient of differential mechanism, reduce pulsation simultaneously and impact, reach the cross-country requirement of automobile.The present invention is specially adapted to various industrial wheeled equipments such as offroad vehicle and dump truck, wheel loader, bulldozer.
Description of drawings
Fig. 1 is the structural representation that non-cone gear differential mechanism is formed;
The 1-differential casing, 2-non-circular planetary gear, the non-round differential gear of 3-, 4-one word axle
Fig. 2 is the non-cone gear differential mechanism gear engagement of a present invention schematic representation.
Embodiment
The invention will be further described below in conjunction with accompanying drawing.
As shown in Figure 1, it is made up of differential carrier 1, non-circular planetary gear 2, non-round differential gear 3, planetary pinion 2 links and can rotate to it with housing by a footstalk or a word axle 4, non-circular planetary gear and non-round differential gear gear ratio are 1: 2, and non-circular planetary gear and non-round differential gear adopt non-cone gear structure.
Embodiment: non-circular planetary gear and non-round differential gear velocity ratio rule are pressed following formula
Set, wherein: i
32Be differential gear and planetary velocity ratio, z
2, z
3Be respectively the planetary pinion and the differential gear number of teeth,
Be the planetary pinion corner, c=0～0.5 is a constant.As shown in Figure 2, non-circular planetary gear 2 and non-round differential gear 3 engagements, the former links by footstalk and housing 1 and is driven by housing.Wherein, z
2=9, zx=18,
C=0.4.
Claims (3)
1. slip-limiting differential mechanism with noncircular bevel gear, it is characterized in that, form by differential carrier, non-circular planetary gear, non-round differential gear, planetary pinion links and can rotate to it by footstalk or a word axle and housing, non-circular planetary gear and non-round differential gear gear ratio are 1: 2, and non-circular planetary gear and non-round differential gear adopt non-cone gear structure.
2. according to the described slip-limiting differential mechanism with noncircular bevel gear of claim 1, it is characterized in that the velocity ratio rule between non-circular planetary gear and the non-round differential gear is will put in order circle according to the corner of non-circular planetary gear to be arranged to 1 period of change.
3. according to the described slip-limiting differential mechanism with noncircular bevel gear of claim 2, it is characterized in that the velocity ratio rule between non-circular planetary gear and the non-round differential gear is pressed following formula
Set, wherein: i
32Be differential gear and planetary velocity ratio, z
2, z
3Be respectively the planetary pinion and the differential gear number of teeth,
Be the planetary pinion corner, c=0～0.5 is a constant.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201010249465 CN101886695A (en) | 2010-08-10 | 2010-08-10 | Slip-limiting differential mechanism with noncircular bevel gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201010249465 CN101886695A (en) | 2010-08-10 | 2010-08-10 | Slip-limiting differential mechanism with noncircular bevel gear |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101886695A true CN101886695A (en) | 2010-11-17 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201010249465 Pending CN101886695A (en) | 2010-08-10 | 2010-08-10 | Slip-limiting differential mechanism with noncircular bevel gear |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102678877A (en) * | 2012-05-25 | 2012-09-19 | 黄革远 | Turntable limited slip differential |
| CN104179926A (en) * | 2014-09-04 | 2014-12-03 | 中国人民解放军军事交通学院 | Non-bevel gear mechanism |
| CN104214304A (en) * | 2014-09-18 | 2014-12-17 | 武汉理工大学 | Arc-tooth non-conical gear antiskid differential mechanism |
| CN104728387A (en) * | 2015-03-27 | 2015-06-24 | 中国人民解放军军事交通学院 | Three-fork-shaft-type noncircular bevel gear limited slip differential |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2628810Y (en) * | 2003-08-18 | 2004-07-28 | 中国人民解放军军事交通学院 | Adaptive gear ratio antisliding differential mechanism |
| CN201475278U (en) * | 2009-09-02 | 2010-05-19 | 李瑞德 | Non-circular bevel gear limited slip differential |
| CN201787026U (en) * | 2010-08-10 | 2011-04-06 | 中国人民解放军军事交通学院 | Noncircular bevel gear limited slip differential |
-
2010
- 2010-08-10 CN CN 201010249465 patent/CN101886695A/en active Pending
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2628810Y (en) * | 2003-08-18 | 2004-07-28 | 中国人民解放军军事交通学院 | Adaptive gear ratio antisliding differential mechanism |
| CN201475278U (en) * | 2009-09-02 | 2010-05-19 | 李瑞德 | Non-circular bevel gear limited slip differential |
| CN201787026U (en) * | 2010-08-10 | 2011-04-06 | 中国人民解放军军事交通学院 | Noncircular bevel gear limited slip differential |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102678877A (en) * | 2012-05-25 | 2012-09-19 | 黄革远 | Turntable limited slip differential |
| CN102678877B (en) * | 2012-05-25 | 2014-11-26 | 黄革远 | Turntable limited slip differential |
| CN104179926A (en) * | 2014-09-04 | 2014-12-03 | 中国人民解放军军事交通学院 | Non-bevel gear mechanism |
| CN104214304A (en) * | 2014-09-18 | 2014-12-17 | 武汉理工大学 | Arc-tooth non-conical gear antiskid differential mechanism |
| CN104214304B (en) * | 2014-09-18 | 2017-03-29 | 武汉理工大学 | Curved tooth not rounded bevel gear limited slip differential |
| CN104728387A (en) * | 2015-03-27 | 2015-06-24 | 中国人民解放军军事交通学院 | Three-fork-shaft-type noncircular bevel gear limited slip differential |
| CN104728387B (en) * | 2015-03-27 | 2017-06-30 | 中国人民解放军军事交通学院 | The slip-limiting differential mechanism with noncircular bevel gear of trident shaft type |
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| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20101117 |