CN1043981A - A kind of drive ratio-changing differential mechanism - Google Patents
A kind of drive ratio-changing differential mechanism Download PDFInfo
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- CN1043981A CN1043981A CN 89100102 CN89100102A CN1043981A CN 1043981 A CN1043981 A CN 1043981A CN 89100102 CN89100102 CN 89100102 CN 89100102 A CN89100102 A CN 89100102A CN 1043981 A CN1043981 A CN 1043981A
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- differential
- cone
- differential mechanism
- planetary pinion
- pitch cone
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Abstract
A kind of drive ratio-changing differential mechanism, it is by driving wheel, transmission shaft, differential mechanism and novel differential gear and planetary pinion are formed.Part number of the present invention and common bevel differential are identical, and structure is simple more than control slip differential limited, and locking coefficient can reach 2.9～3.1.It is long that the present invention has the life-span, low cost and other advantages, and can reduce the tire wear rate of industrial wheeled equipment greatly.The present invention is specially adapted to engineering machinery and offroad vehicles such as loader, bulldozer, vehicles such as dump truck, but and superseded differential lock of large size and high friction differential mechanism.
Description
The invention belongs to mechanical manufacturing field.
Differential mechanism is a vitals in the engineering machinery such as various types of automobiles, loader, and its effect is that two driving wheels of vehicle can be rotated with friction speed, thereby vehicle can be turned.Visible Fig. 1 of differential mechanism principle commonly used, the moment of torsion that distributes on its two driving wheels are basic equating.If one of them driving wheel is trapped in when skidding in the mud, the driving wheel of opposite side does not transmit too big moment of torsion yet, and vehicle also just is difficult to deviate from automatically predicament, and this is the problem that the vehicle regular meeting of travelling on the road surface that is difficult to walk runs into.
In order to overcome this shortcoming, need take some measures, make that the torque distribution on two driving wheels might change as required.The way of using has three at present, and (1) adopts differential lock, and (2) adopt control slip differential limited, and (3) adopt the variable ratio differential mechanism.The benefit that adopts differential lock is that the locking coefficient maximum value of the ratio of fast runner transmitting torque (the slow-speed wheel with) is for infinitely great, shortcoming is that differential lock has only when vehicle sticks and could engage, use very inconveniently, and vehicle lost inertia after sticking, will transfer to mud ground to be not easy again.In addition, just turn, overturn accident then takes place easily if the driver has forgotten to open differential lock.Structurally also need an additional cover operation equipment in addition.
The locking coefficient of control slip differential limited also can be done greatlyyer, but their complex structure, and working life is short, neither a kind of desirable structure.
The main feature of variable ratio differential mechanism is to have adopted the differential gear profile of tooth of particular design, when trend appears skidding in a side drive wheel, it can change slightly soon than opposite side wheel, this moment, above-mentioned special tooth profile impelled the planet wheel in the differential mechanism to depart from the equilibrium position, and make the moment of torsion that is assigned on fast runner and the slow-speed wheel not wait (little on the fast runner, on the slow-speed wheel greatly) thus played the effect that prevents skidding.Because this differential mechanism only need change tooth-formation of gear and not increase other part, so simple in structure, easy to use.
But the performance of the variable ratio differential mechanism of external at present development and use is not high, locking coefficient can only reach 1,5, the differential mechanism of using on the car of the big Dodge of the U.S. for example, can not satisfy the needs of most of vehicles that on abominable road surface, travel, this in addition tooth-formation of gear processing difficulties, general factory can't make, thereby application is not extensive, can't replace differential lock or control slip differential limited.
The present invention is exactly at above-mentioned deficiency, and it is bigger to develop a kind of locking coefficient, the better variable ratio differential mechanism of performance.
Drive ratio-changing differential mechanism provided by the present invention is made up of driving wheel, transmission shaft, differential mechanism, differential gear, planetary pinion etc., its main points be differential gear and planetary pinion pitch cone with the top flank profil for its couple gear pitch cone with the bottom flank profil by (d φ
(1))/(d φ
(2))=(Z
2)/(Z
1) [1-cratsin (Z
2Φ
(2)+ C (1-rat) sin (3Z
2Φ
(2))] conjugate tooth profiles that obtain of the characteristics of motion that provides, Z
1-half shaft wheel the number of teeth, Z
2-planet wheel the number of teeth, Φ
(1)-half shaft wheel corner, Φ
(2)-planet wheel corner, C-velocity ratio variation coefficient, its optimum valuing range can be 0.12～0.20, the rat-partition coefficient, it gets optimum valuing range is 0.90～1, differential gear and planetary pinion pitch cone are respectively the part that the vertex of a cone is positioned at two tangent conical surfaces on pitch cone summit with the bottom tooth surface shape, and vertex of a cone half-angle is used respectively
(1)And
(2)Represent
(2)Optimum valuing range can be 30 °～60 °,
(1)Then by ┏
(1)=tg-1 1/ (kp-ctg ┏
(2)) determine that Kp represents the induced normal curvature at pitch cone place in the formula.
Planetary pinion the circular thickness at pitch cone place by
Determine.And do not allow attenuate, L in the formula
oThe Outer cone distance of-gear pair.Differential gear in the circular thickness at pitch cone place by f
(1) P=(3 π-2c (4rat-1))/(3Z
1)
Determine, in the formula
SPt-reserves circumferential sideshake.
Part number of the present invention and common bevel differential are identical, and structure is simple more than control slip differential limited, and locking coefficient can reach 2.9～3.1, and sideshake is even.It is long that the present invention has the life-span, and low cost and other advantages also can alleviate the labor intensity of driver simultaneously and improve the passing capacity of vehicle on the road surface that is difficult to walk, and improves operating efficiency, and reduces the tire wear rate of industrial wheeled equipment greatly.Gear in this differential mechanism adds and can the bilateral flank profil be shaped simultaneously man-hour on the Bao tooth machine through repacking, manufacturing efficiency is not less than the bevel gear in the open differential, the present invention is specially adapted to loader, engineering machinery and offroad vehicles such as bulldozer, vehicles such as dump truck, and but large size eliminates differential lock and high friction differential mechanism, makes the updating and upgrading of a product.
Embodiment: the variable ratio differential mechanism on the ZL40 loader
Its Z
1=12, Z
2=7,
=24 °, c=0.16, rat=0.98, ┌
(2)=45.4 °, reference cone bus length=74.79mm, the back cone of differential gear launches the height h in the profile of tooth
1Expression, chordal thickness s
1Expression, planetary back cone launches the height h in the profile of tooth
2Expression, chordal thickness s
2Expression, data see Table 1.
Table 1
H
1S
1H
2S
2
8.762 6.903 10.968 7.006
7.213 8.718 8.896 10.444
3.981 11.800 6.922 12.232
-0.226 15.227 3.516 14.537
-4.335 18.073 -0.817 16.807
-7.342 19.860 -3.041 17.755
-9.037 2.0716 -7.015 19.109
-9.370 19.710
Accompanying drawing 1 is a variable ratio differential mechanism sketch.(1) is driving wheel among the figure, and (2) are transmission shafts, and (3) are differential mechanisms, and (4) are differential gears, and (5) are planetary pinions.
Accompanying drawing 2 is differential gear schematic representation.(6) are pitch cones among the figure, (7) be pitch cone with the top flank profil, (8) be pitch cone with the bottom flank profil, (9) are the pitch cone summits.
Accompanying drawing 3 is planetary pinion schematic representation, and (6) are pitch cones among the figure, (7) be pitch cone with the top flank profil, (8) be pitch cone with the bottom flank profil, (9) are the pitch cone summits.
Accompanying drawing 4 is that the back cone of differential gear launches profile of tooth, and (10) are highly to use h among the figure
1Expression, (11) are chordal thickness s
1Expression.
Accompanying drawing 5 is that planetary back cone launches profile of tooth, and (12) are highly to use h among the figure
2Expression, (13) are chordal thickness s
2Expression.
Claims (5)
1, a kind of drive ratio-changing differential mechanism, it is made up of driving wheel (1), transmission shaft (2), differential mechanism (3), differential gear (4), planetary pinion (5), it is characterized in that differential gear and planetary pinion pitch cone (6) are that its couple gear pitch cone is pressed (d φ (1))/(d φ (2))=(Z2)/(Z1) with bottom flank profil (8) with top flank profil (7)
[1-cratsin (Z
2Φ
(2))+C (1-rat) sin (3Z
2Φ
(2))] conjugate tooth profiles that the characteristics of motion that provides obtains, differential gear and planetary pinion pitch cone are respectively the part that the vertex of a cone is positioned at two tangent circular cones on pitch cone summit (9) with the bottom tooth surface shape.
2,, it is characterized in that the vertex of a cone half-angle ┌ of differential gear reference cone with the bottom flank of tooth according to the described variable ratio differential mechanism of claim 1
(1)With the vertex of a cone half-angle ┌ of planetary pinion reference cone with the bottom flank of tooth
(2)Obey ┏
(1)=tg
-11/ (kp-ctg ┏ (2)) relation, k
pThe induced normal curvature at expression pitch cone place, ┌
(2)Optimum valuing range can be 30 °～60 °.
3, according to claim 1,2 described variable ratio differential mechanisms, it is characterized in that differential gear in the circular thickness at pitch cone place by fp
(1)=(3 π-2c (4rat-1))/(3Z
1) L
0Cos
0 (2)-Spt determines, planetary pinion in the circular thickness at pitch cone place by fp
(2)=(π L
1)/(Z
2) sin θ
0 (2)Determine, and do not allow attenuate.
4,, it is characterized in that the optimum valuing range of c in the formula can be 0.12～0.20, the optimum valuing range of rat can be 0.90～1 according to claim 1,2 described variable ratio differential mechanisms.
5,, it is characterized in that the optimum valuing range of c in the formula can be 0.12～0.20, the optimum valuing range of rat can be 0.90～1 according to the described variable ratio differential mechanism of claim 3.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 89100102 CN1021360C (en) | 1989-01-05 | 1989-01-05 | Drive ratio-changing differential mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 89100102 CN1021360C (en) | 1989-01-05 | 1989-01-05 | Drive ratio-changing differential mechanism |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1043981A true CN1043981A (en) | 1990-07-18 |
| CN1021360C CN1021360C (en) | 1993-06-23 |
Family
ID=4853693
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 89100102 Expired - Fee Related CN1021360C (en) | 1989-01-05 | 1989-01-05 | Drive ratio-changing differential mechanism |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1021360C (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2003042583A1 (en) * | 2001-11-14 | 2003-05-22 | Xiaochun Wang | Limited slip differential of variable gear ratio type |
| CN100567066C (en) * | 2007-12-13 | 2009-12-09 | 南京航空航天大学 | Combined type obstacle crossing walking system |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1324251C (en) * | 2003-08-18 | 2007-07-04 | 中国人民解放军军事交通学院 | Anti-skid differential with adaptive speed ratio |
-
1989
- 1989-01-05 CN CN 89100102 patent/CN1021360C/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2003042583A1 (en) * | 2001-11-14 | 2003-05-22 | Xiaochun Wang | Limited slip differential of variable gear ratio type |
| CN100567066C (en) * | 2007-12-13 | 2009-12-09 | 南京航空航天大学 | Combined type obstacle crossing walking system |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1021360C (en) | 1993-06-23 |
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| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
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| C14 | Grant of patent or utility model | ||
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