CN2553194Y - Variable transmission ratio slide-limiting differential mechanism - Google Patents

Abstract

The utility model relates to an anti-slip differential with a variable drive ratio. The purpose is to provide a new anti-slip differential with a big drive ratio and a higher locking coefficient, which cross-country power can be greatly increased under way. The technical proposal is that the differential comprises a case, in which a planetary gear and a half axle gear are arranged; a flat washer is arranged outside the half axle gear; the teeth on the planetary gear and the half axle gear adopt the variable drive ratio structure with three teeth as a group; the outlines of the three teeth are a high tooth and two low teeth with same height in turn or two high teeth with same height or a low tooth; a disc spring is arranged between the flat washer outside the half axle gear and the case. The utility model is particularly suitable for the wheel engineering machine, such as the cross-country vehicle, the dump truck and the wheel loader.

Description

Differential mechanism with variable transmission ratio and eliminating slip

The utility model relates to a kind of vehicle limited slip differential, is specifically related to a kind of differential mechanism with variable transmission ratio and eliminating slip.

The structure of limited slip differential has various ways at present, it is several that working principle can reduce interior friction type, override type, the deceleration of electrons anti-slip differential system that combines with the ABs brake system and potential barrier formula, they exist different shortcomings separately, as costing an arm and a leg of the high-friction-type in the interior friction, steering drag is bigger, and tire wear is very fast; The poor reliability of override type is moved not steady; The power consumption of braking antiskid system is bigger; Potential barrier formula drive ratio-changing differential mechanism has simple in structure, the advantage of reliable performance, but because its gear ratio cycle is a circular pitch, though can improve its speed ratio wave range to a certain extent by parameter optimization, but effect is limited, further improving variator ratio range will make the relative curvature between the flank of tooth increase rapidly, even on the flank of tooth, produce crest line, by traditional design method, planetary pinion is 7 teeth, differential gear is that the variator ratio range between the variable ratio differential mechanism two halves arbor wheel of 12 teeth has only 1: 1.38, planetary pinion is 9 teeth, and differential gear is that the differential mechanism of 12 teeth only can arrive 1: 1.31, still dislikes not enough for offroad vehicle.

It is big and have higher locking coefficient, the differential mechanism with variable transmission ratio and eliminating slip unsettled or that cross-country power strengthens significantly when ice and snow road is advanced at one-sided driving wheel that the purpose of this utility model provides a kind of gear ratio.

For achieving the above object, technical solution of the present utility model is, a kind of differential mechanism with variable transmission ratio and eliminating slip, comprise differential carrier 1, the planetary pinion 5 and the differential gear 2 that are provided with in it, differential gear 2 is outside equipped with flat gasket 3, and its special way is: tooth corresponding on described planetary pinion 5 and the differential gear 2 is the tooth-shape structure of one group in three teeth.

The profile of tooth of three teeth is followed successively by high tooth and two contour low teeth, is shallow slot between high tooth and the low tooth, is deep trouth between two low teeth.

The profile of tooth of three teeth is followed successively by two contour high teeth and low tooth, is shallow slot between two high teeth, is deep trouth between high tooth and the low tooth.

The flat gasket 3 and 1 of the differential carrier in described differential gear 2 outsides add disc spring film 4.

The speed ratio Changing Pattern of described gear pair is: $\frac{d{\mathrm{\φ}}^{\left(1\right)}}{{\mathrm{d\φ}}^{\left(2\right)}}=\frac{z_2}{z_1}[1-C*\mathrm{rat}*\sin (z_2{\mathrm{\φ}}^{\left(2\right)}/3)+C*(1-\mathrm{rat})*\sin (z_2*{\mathrm{\φ}}^{\left(2\right)})]$ Z in the formula ₁Be the half shaft wheel number of teeth, Z ₂Be the planetary pinion number of teeth, Ф ⁽¹⁾Be half shaft wheel corner, Ф ⁽²⁾Be the planet wheel corner.

Compared with prior art, the utility model has the advantages that:

1, this differential mechanism is a kind of three circular pitch variable ratio differential mechanisms, and its planetary pinion and differential gear are done the variable ratio transmission, and the geometric parameter of the same side flank of tooth has nothing in common with each other in same group, and the period of change of velocity ratio is three circular pitches.Owing to change the speed ratio cycle into three circular pitches, thereby reduced the relative angle acceleration between planetary pinion and differential gear significantly, make speed ratio between the two halves arbor wheel reach 1: 1.85 the phenomenon that the flank of tooth comes to a point does not still take place, increased substantially the locking coefficient of differential mechanism.

2, installing disc spring film additional between flat gasket outside differential gear and differential carrier entad loads, differential gear is pressed to planetary pinion, make vehicle opposite side wheel when the unsettled or one-sided driving wheel of one-sided driving wheel is on ice and snow road still have certain output torque, thereby strengthen the cross-country power of vehicle significantly.If it is do not adopt preloaded spring,, unsettled or when being positioned on the ice and snow road, its frictional resistance moment is zero or almost nil when fast runner although newly-designed profile of tooth can make slow-speed wheel moment of torsion reach the several times of fast runner.Even amplified several times by the variable ratio differential mechanism, the moment of torsion that is assigned on the slow-speed wheel still is not enough to powered vehicle, opens the throttle to make the fast runner that skids fly to change.After increasing disc spring film, after the friction torque that is produced between differential gear and the differential carrier is amplified several times by the variable ratio differential gear, still can keep the slow-speed wheel and go up certain driving moment, promote vehicle and advance.When bridge carries increase, the axial force on the half shaft wheel will overcome spring thrust, flatten disc spring film, keep necessary flank of tooth sideshake, prevent flank of tooth premature wear.

The accompanying drawing drawing is described as follows:

Fig. 1 is a structural representation of the present utility model;

Fig. 2 is the structural representation of differential gear in the utility model gear pair;

Fig. 3 is a planetary structural representation in the utility model gear pair.

Description of reference numerals is as follows: the 1-differential carrier, and the 2-differential gear, the 3-flat gasket, the 4-disc spring film, the 5-planetary pinion, the 6-cross axle, the 7-spherical pad, the high tooth of 8-, 9-hangs down tooth, the 10-shallow slot, the 11-deep trouth, the 12-deep trouth, the 13-shallow slot, the high tooth of 14-, 15-hangs down tooth.

The utility model is described in further detail below in conjunction with accompanying drawing:

A kind of differential mechanism with variable transmission ratio and eliminating slip, comprise differential carrier 1, in differential carrier 1, be arranged at planetary pinion 5 and differential gear 2 on the cross axle 6, planetary pinion 5 is outside equipped with spherical pad 7, differential gear 2 is outside equipped with flat gasket 3, said planetary pinion 5 and differential gear 2 constitute gear pair, tooth corresponding on the gear pair is the tooth-shape structure of one group in three teeth, the profile of tooth of three teeth is followed successively by high tooth and two contour low teeth, be shallow slot 10 between high tooth 8 and the low tooth 9 on the differential gear 2, between two low teeth 9 is deep trouth 11, be to be deep trouth 12 between 13, two low teeth 15 of shallow slot between high tooth 14 and the low tooth 15 on the planetary pinion 5.The speed ratio Changing Pattern of this routine middle gear pair is: $\frac{d{\mathrm{\φ}}^{\left(1\right)}}{{\mathrm{d\φ}}^{\left(2\right)}}=\frac{z_2}{z_1}[1-C*\mathrm{rat}*\sin (z_2{\mathrm{\φ}}^{\left(2\right)}/3)+C*(1-\mathrm{rat})*\sin (z_2*{\mathrm{\φ}}^{\left(2\right)})]$ Z in the formula ₁Be the half shaft wheel number of teeth, Z ₂Be the planetary pinion number of teeth, Ф ⁽¹⁾Be half shaft wheel corner, Ф ⁽²⁾Be the planet wheel corner, be equipped with disc spring film 4 between the flat gasket 3 in said differential gear 2 outsides and the differential carrier 1.

Working principle of the present utility model is as follows: utilize between the half shaft wheel of both sides periodic velocity ratio to fluctuate and cause a potential barrier to differential motion, have only when the difference in torque of both sides half shaft wheel during greater than the potential barrier of velocity ratio and friction torque sum, differential gear can be crossed the continuous differential movement of potential barrier, otherwise can only swing in a transmission fluctuation ratio cycle.

Claims (5)

1, a kind of differential mechanism with variable transmission ratio and eliminating slip, comprise differential carrier (1), the planetary pinion (5) and the differential gear (2) that are provided with in it, differential gear (2) is outside equipped with flat gasket (3), it is characterized in that: it is the tooth-shape structure of one group in three teeth that described planetary pinion (5) and differential gear (2) are gone up corresponding tooth.

2, differential mechanism with variable transmission ratio and eliminating slip as claimed in claim 1 is characterized in that: the profile of tooth of described three teeth is followed successively by high tooth and two contour low teeth, is shallow slot between high tooth and the low tooth, is deep trouth between two low teeth.

3, differential mechanism with variable transmission ratio and eliminating slip as claimed in claim 1 is characterized in that: the profile of tooth of described three teeth is followed successively by two contour high teeth and low tooth, is shallow slot between two high teeth, is deep trouth between high tooth and the low tooth.

4, as claim 1 or 2 or 3 described differential mechanism with variable transmission ratio and eliminating slip, it is characterized in that: be equipped with disc spring film (4) between the flat gasket (3) in described differential gear (2) outside and differential carrier (1).

5, differential mechanism with variable transmission ratio and eliminating slip as claimed in claim 4 is characterized in that: the speed ratio Changing Pattern of described gear pair is: $\frac{d{\mathrm{\φ}}^{\left(1\right)}}{{\mathrm{d\φ}}^{\left(2\right)}}=\frac{z_2}{z_1}[1-C*\mathrm{rat}*\sin (z_2{\mathrm{\φ}}^{\left(2\right)}/3)+C*(1-\mathrm{rat})*\sin (z_2*{\mathrm{\φ}}^{\left(2\right)})]$ Z in the formula ₁Be the half shaft wheel number of teeth, Z ₂Be the planetary pinion number of teeth, Ф ⁽¹⁾Be half shaft wheel corner, Ф ⁽²⁾Be the planet wheel corner.

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