CN1324251C - Anti-skid differential with adaptive speed ratio - Google Patents
Anti-skid differential with adaptive speed ratio Download PDFInfo
- Publication number
- CN1324251C CN1324251C CNB031341144A CN03134114A CN1324251C CN 1324251 C CN1324251 C CN 1324251C CN B031341144 A CNB031341144 A CN B031341144A CN 03134114 A CN03134114 A CN 03134114A CN 1324251 C CN1324251 C CN 1324251C
- Authority
- CN
- China
- Prior art keywords
- differential
- gear
- planet gear
- ratio
- semi
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Images
Landscapes
- Retarders (AREA)
Abstract
The present invention relates to an anti-skid differential with an adaptive variation ratio, which is composed of a differential casing, four planet gears, two semi-shaft gears and a cross-shaped planet gear shaft which are assembled together. The present invention is characterized in that torque distribution can be automatically regulated according to the rotation speed condition of wheels of a left and a right sides. The drive ratio between the planet gear and the semi-shaft gear meets (reference to a formula 1) that phi 1 and phi 2 are respectively the turning angle of the planet gear and the turning angle of the semi-shaft gear; z1 and z2 are respectively the tooth number of the planet gear and the semi-shaft gear; c is a constant; n is the ratio change period of each circle of the planet gear. The present invention makes a breakthrough that the ratio change period is gear single-circle limitation. The drive ratio changing rule of the planet gear is arranged within the complete circle interval of the planet gear. Thus, the value change range can be greatly enhanced so as to enhance the locking coefficient of the differential and reduce pulsation and an impact simultaneously. Thus, requirements of crossing the country for an automobile and preventing skid can be achieved. The present invention is particularly suitable for various wheeled type engineering machines, such as cross-country automobiles, dump automobiles, wheel loaders, bulldozers, etc.
Description
(1) technical field
The present invention relates to a kind of differential mechanism, particularly a kind ofly in the whole circle of planet wheel interval, its velocity ratio Changing Pattern is set, improve the numerical value change scope, thereby improve the gear ratio differential mechanism of differential mechanism locking coefficient.
(2) 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 as shown in Figure 1, 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 that has used 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 gear circular pitch, and its cycle is too short, and amplitude of variation is too little.
(3) summary of the invention
The technical problem to be solved in the present invention is to overcome the shortcoming and defect that above-mentioned all kinds of differential mechanism exists, and develops a kind of brand-new adaptive rate than limited slip differential, improves the locking coefficient of differential mechanism, reduces pulsation and impact, reaches the cross-country requirement of automobile.
The technological scheme that adopts is:
Adaptive rate is than limited slip differential, comprises differential casing, 2 differential gears, 4 planetary pinions, cross planet pin.Differential casing is middle minute two style structure, and the centre is provided with cross bore.On the cross planet pin, load onto planetary pinion respectively.In the left and right chamber of differential casing, be respectively charged into a differential gear and spring, friction plate.A left side half housing and right half housing of differential casing are connected in aggregates by bolt.Left and right half gear internal spline is connected with the left and right sides semiaxis key of ransaxle respectively.Planetary pinion one circle has one or three periods of change, and differential gear one circle has two or four periods of change.The present invention can regulate torque automatically according to the speed conditions of and arranged on left and right sides wheel, thereby effectively utilizes adhesion of wheels, reaches skidproof effect, and the velocity ratio of planetary pinion and differential gear satisfies:
In the formula,
1,
2---planetary pinion and differential gear corner, z
1, z
2---the planetary pinion and the differential gear number of teeth, c---constant, n=1 or 3---the every Lap Time of planetary pinion compares period of change.
Above-mentioned C span can be 0.2-0.45.
The present invention has broken through the speed ratio period of change and has been the restriction of gear single-revolution, in the whole circle of planetary pinion interval, its velocity ratio Changing Pattern is set, can improves its numerical value change scope greatly like this, thereby improve the locking coefficient of differential mechanism, reduce pulsation and impact simultaneously, reach the cross-country and skid-resistance requirements of automobile.Be specially adapted to various industrial wheeled equipments such as offroad vehicle, dump truck, wheel loader, bulldozer.
(4) description of drawings
Fig. 1 is known symmetrical bevel differential structural representation.
Fig. 2 is an a kind of embodiment's of the present invention structural representation.
Fig. 3 works as z
1=9, z
2=12, the speed ratio change curve when c=0.3, n=3.
Fig. 4 works as z
1=9, z
2=18, the speed ratio change curve when c=0.4, n=1.
(5) embodiment
Embodiment one
Adaptive rate comprises differential casing, 4 planetary pinions 1,2 differential gears 2, cross planet pin 3 and dish springs 4 than the sliding device of anti-slippage.Differential casing is made up of a left side half housing 5, right half housing 6, and there is cross bore the centre.After 4 planetary pinions 1 are installed on the cross axle of planet pin 3 respectively, in the differential casing of packing into.Be respectively charged into a differential gear 2 in each die cavity of the left side of differential casing half housing 5 and right half housing 6, dish spring 4 and pad 7 connect into an overall structure with 8 bolts with a left side half housing 5 and right half housing 6 then.Planetary pinion 1 every circle has three speed ratio periods of change.Planetary pinion 1 satisfies with the velocity ratio of differential gear 2:
In the formula,
1,
2Be respectively planetary pinion and differential gear corner, z
1, z
2Be respectively the planetary pinion and the differential gear number of teeth, c is a constant, and n is that the every Lap Time of planetary pinion compares period of change.Z wherein
1=9, z
2=12 (ratio that is the number of teeth and the number of teeth of differential gear 2 of planet gear 1 is 3: 4), c=0.3, n=3.Its speed ratio change curve is seen Fig. 3.
Embodiment two
Adaptive rate is structurally more basic identical with embodiment one than limited slip differential embodiment two, and institute's difference is that this adaptive rate has a speed ratio period of change, the z of this differential mechanism than planetary pinion 1 every circle of limited slip differential
1=9, z
1=18 (ratio that is the number of teeth and the number of teeth of differential gear 2 of planet gear 1 is 1: 2), c=0.4, n=1.
Claims (2)
1, adaptive rate is than limited slip differential, and it is made up of differential carrier, 4 planetary pinions, 2 differential gears and cross planet pin, it is characterized in that the velocity ratio between planetary pinion and the differential gear changes, and satisfies:
In the formula,
1,
2Be respectively planetary pinion and differential gear corner, z
1, z
2Be respectively the planetary pinion and the differential gear number of teeth, the ratio of the two is 1: 2 or 3: 4, and c is a constant, n=1 or 3, for the every Lap Time of planetary pinion than period of change, the phase number of teeth is 2,4,5,6 or 7 weekly, the tooth-shape structure that does not comprise one group in three teeth, promptly the speed ratio period of change be three teeth except.
2, according to the described adaptive rate of claim 1 than limited slip differential, it is characterized in that the span of constant c in the formula is: 0.2～0.45.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB031341144A CN1324251C (en) | 2003-08-18 | 2003-08-18 | Anti-skid differential with adaptive speed ratio |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB031341144A CN1324251C (en) | 2003-08-18 | 2003-08-18 | Anti-skid differential with adaptive speed ratio |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1487222A CN1487222A (en) | 2004-04-07 |
| CN1324251C true CN1324251C (en) | 2007-07-04 |
Family
ID=34154393
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB031341144A Expired - Fee Related CN1324251C (en) | 2003-08-18 | 2003-08-18 | Anti-skid differential with adaptive speed ratio |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1324251C (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1324253C (en) * | 2004-07-13 | 2007-07-04 | 武汉理工大学 | Locking coefficient self-adjusted anti-skid differential mechanism |
| FR2909065B1 (en) * | 2006-11-27 | 2009-07-10 | Peugeot Citroen Automobiles Sa | STEERING DEVICE FOR IMPROVING THE POWER OF A VEHICLE. |
| CN101555935B (en) * | 2009-05-22 | 2011-11-02 | 中国人民解放军军事交通学院 | Variation-ratio non-circular planetary gear limited slip differential (LSD) |
| 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 |
| CN107420518A (en) * | 2017-09-11 | 2017-12-01 | 宁波市鄞州益定机械制造有限公司 | A kind of limited-slip differential assembly |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1021360C (en) * | 1989-01-05 | 1993-06-23 | 西安交通大学 | Drive ratio-changing differential mechanism |
| CN1418784A (en) * | 2001-11-14 | 2003-05-21 | 王小椿 | Differential mechanism with variable transmission ratio and eliminating slip |
| CN2553194Y (en) * | 2001-11-14 | 2003-05-28 | 王小椿 | Variable transmission ratio slide-limiting differential mechanism |
| CN2553193Y (en) * | 2001-11-08 | 2003-05-28 | 沈阳华德汽车贸易有限公司 | Variable transmission ration slide-limiting differential mechanism assembly |
| 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 |
-
2003
- 2003-08-18 CN CNB031341144A patent/CN1324251C/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1021360C (en) * | 1989-01-05 | 1993-06-23 | 西安交通大学 | Drive ratio-changing differential mechanism |
| CN2553193Y (en) * | 2001-11-08 | 2003-05-28 | 沈阳华德汽车贸易有限公司 | Variable transmission ration slide-limiting differential mechanism assembly |
| CN1418784A (en) * | 2001-11-14 | 2003-05-21 | 王小椿 | Differential mechanism with variable transmission ratio and eliminating slip |
| CN2553194Y (en) * | 2001-11-14 | 2003-05-28 | 王小椿 | Variable transmission ratio slide-limiting differential mechanism |
| 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 |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1487222A (en) | 2004-04-07 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN1324251C (en) | Anti-skid differential with adaptive speed ratio | |
| CN1215946C (en) | Differential mechanism with variable transmission ratio and eliminating slip | |
| CN2570085Y (en) | Differential transferring equipment of shell-less differential gear | |
| CN200981502Y (en) | Rear axle main reducing gear assembly for MPV/SUV vehicle | |
| CN2628810Y (en) | Adaptive gear ratio antisliding differential mechanism | |
| WO2008055062A2 (en) | Steer drive for tracked vehicles | |
| CN101886695A (en) | Slip-limiting differential mechanism with noncircular bevel gear | |
| CN2570086Y (en) | Differential transferring equipment of single differential gear | |
| CN201475278U (en) | Non-circular bevel gear limited slip differential | |
| CN201296167Y (en) | Power transmission system for four-wheel drive motor vehicle | |
| CN201787026U (en) | Noncircular bevel gear limited slip differential | |
| CN2552756Y (en) | Vehicular friction plate self-locking antiskid differential | |
| CN201003592Y (en) | Automobile differential gear locking arrangement | |
| CN204512354U (en) | The slip-limiting differential mechanism with noncircular bevel gear of Cardon universal joint | |
| CN1009944B (en) | Automatic antiskid differential for motor vehicles and wheel type tractors | |
| CN1021360C (en) | Drive ratio-changing differential mechanism | |
| CN1225374C (en) | Frequently interlocked universal differential driver | |
| CN201090708Y (en) | Drive axle with differential lock | |
| CN201281118Y (en) | Automatic antiskid differential | |
| CN2476469Y (en) | Vehicle brake auxiliary device | |
| CN1064607C (en) | Composite high-passage differential transmission mechanism | |
| CN105599603A (en) | Rear steering drive axle assembly of forklift | |
| CN2553193Y (en) | Variable transmission ration slide-limiting differential mechanism assembly | |
| CN2623500Y (en) | Double diagonal line differential mechanism of four-wheel drive vehicle | |
| CN203822998U (en) | Simple mechanical differential lock |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20070704 Termination date: 20150818 |
|
| EXPY | Termination of patent right or utility model |