CN201858328U - Noncircular planetary gear limited-slip differential - Google Patents

Abstract

The utility model discloses a noncircular planetary gear limited-slip differential. The noncircular planetary gear limited-slip differential comprises a first noncircular sun gear, a second noncircular sun gear, a duplex noncircular planetary gear and a planet carrier, wherein the planet carrier is used for outputting power, the first noncircular sun gear and the second noncircular sun gear are fixedly connected with a front output shaft and a rear output shaft, and when relative movement exists between the gears, the transmission ratio between the front output shaft and the rear output shaft is determined according to the transmission ratio relationship of the noncircular gears. Compared with the ordinary cylindrical planetary gear differential, the noncircular planetary gear limited-slip differential has the following differences: when the relative movement exists between the gears, the transmission ratio between the front output shaft and the rear output shaft is not a fixed value any more and determined according to the transmission ratio relationship of the noncircular gears, and the ratio of output torque of the front output shaft and the rear output shaft is changed correspondingly, so that the driving force provided by the output shaft with good adhesion can be fully utilized, and the purpose of improving the trafficability of vehicles is further achieved.

Description

Non-circular planetary gear limited slip differential

Technical field

The utility model belongs to the system of vehicle transmission field, is specifically related to a kind of automobile differential mechanism of forming with non-circular planetary gear.

Background technique

Offroad vehicle travels through be everlasting bad road or cross-country locality, for improving passing ability, generally adopts multiaxis to drive.Be rigid joint if be unkitted interaxial differential between the antero posterior axis, then when automobile running, front and back wheel will be with same angular velocity rotation.Because tire pressure, load are not the same, when particularly travelling on uneven road surface, the stroke that front and back wheel was passed through in the unit time is unequal, thereby causes trackslipping or slippage of wheel, causes power cycle but in actual use.

Differential mechanism is installed between live axle can be avoided above-mentioned phenomenon.But common cylindrical planetary gear differential mechanism will reduce the passing ability of wheel significantly, its reason is that the transfer case output torque distributes to each output shaft than ground surely by the differential mechanism velocity ratio, when wheel-slip wherein, this adhesion of wheels reduces, driving force reduces thereupon, other driving force also reduces thereupon in proportion, causes trafficability to reduce.

The model utility content

The purpose of this utility model is to provide a kind of planetary gear differential device with the sliding function of limit, does not limit problem sliding, that cause the vehicle passing capacity to reduce to solve the common cylinder satellite differential.

The non-circular planetary gear limited slip differential of the utility model, form by the first non-round central gear, the second non-round central gear, duplex non-circular planetary gear and planet carrier, planet carrier input power, the first and second non-round central gears connect firmly with forward and backward output shaft respectively, when having relative movement between gear, the velocity ratio of former and later two output shafts is determined by velocity ratio relation between the noncircular gear.

The first and second non-round central gear structures are identical, and the duplex non-circular planetary gear has three groups and evenly distribute 90 ° of duplex non-circular planetary gear phase phase differences around described non-round central gear.

Duplex non-circular planetary gear and non-round central gear velocity ratio rule are pressed following formula

Selected, wherein: i ₃₁Be the velocity ratio of duplex non-circular planetary gear and non-round central gear, z ₁, z ₃Be respectively the non-round central gear and the duplex non-circular planetary gear number of teeth,

Be non-round central gear corner, c=0～0.5 is a constant.

The utility model is compared with the common cylinder satellite differential, its difference is: when having relative movement between gear, the velocity ratio of former and later two output shafts no longer is a definite value, but according to the rule cycle variation of setting, correspondingly, the ratio of diaxon output torque also changes thereupon, thereby the driving force that the good output shaft that can make full use of adhesion provides reaches the purpose of improving the cross-country passing ability of vehicle.

Description of drawings

Figure 1 shows that common cylinder satellite differential schematic representation;

Fig. 2 is the utility model non-circular planetary gear differential mechanism schematic representation;

Fig. 3 is the pitch curve of the first non-round central gear and the non-round planet wheel transmission of duplex;

Fig. 4 is the pitch curve of the second non-round central gear and the non-round planet wheel transmission of duplex;

Fig. 5 is the first non-round central gear and duplex non-circular planetary gear transmission schematic representation;

Fig. 6 is the second non-round central gear and duplex non-circular planetary gear transmission schematic representation.

Embodiment

The utility model is described in further detail below in conjunction with drawings and Examples.

Figure 1 shows that the common cylinder satellite differential, comprise its transformation mechanism velocity ratio of gear 1, gear 2, duplicate gear 3 and planet carrier (output shaft II is with respect to output shaft I):

$i_{21}^H=\frac{r_{31}\·r_2}{r_1\·r_{32}}=c_1$

In the formula, Expression transformation mechanism velocity ratio, r ₁, r ₂, r ₃₁, r ₃₂Be respectively gear 1, gear 2, with the duplicate gear 3 of gear 1 engagement, with the Pitch radius of the duplicate gear 3 of gear 2 engagements, be definite value, c ₁Be constant.

Figure 2 shows that the non-circular planetary gear differential mechanism that the utility model is related, because each gear pitch curve no longer is round, its transformation mechanism velocity ratio:

No longer be definite value, and become duplex non-circular planetary gear corner

The periodic function of (around axis own).

This effect can make full use of the adhesion on wheel and ground, improves the passing ability of vehicle.

Of particular note, the non-circular planetary gear differential mechanism has adaptivity in function aspects, after promptly assembling, no longer needs manual intervention, distribute but regulate output torque automatically according to wheel-slip situation on the different axletrees, the ratio maximum value of its output torque is called locking coefficient.

Figure 2 shows that the non-circular planetary gear differential mechanism sketch that the utility model is related, Fig. 3 is the pitch curve of the first non-round central gear 11 and non-round planet wheel 3 transmissions of duplex, and Fig. 4 is the pitch curve of the second non-round central gear 12 and non-round planet wheel 13 transmissions of duplex.Non-circular planetary gear limited slip differential, form by first non-round central gear 11, the second non-round central gear 12, duplex non-circular planetary gear 13 and planet carrier 14, planet carrier input power, the first and second non-round central gears connect firmly with forward and backward output shaft respectively, when having relative movement between gear, the velocity ratio of former and later two output shafts is determined by velocity ratio relation between the noncircular gear.Embodiment: as shown in Figure 5, get z ₁=z ₂=18, z ₃=12, C=0.3.Fig. 5 is the first non-round central gear 11 and duplex non-circular planetary gear 13 transmission schematic representation, and Fig. 6 is the second non-round central gear 12 and duplex non-circular planetary gear 13 transmission schematic representation.

Claims (3)

1. non-circular planetary gear limited slip differential, it is characterized in that: form by the first non-round central gear, the second non-round central gear, duplex non-circular planetary gear and planet carrier, planet carrier input power, the first and second non-round central gears connect firmly with forward and backward output shaft respectively.

2. according to the described non-circular planetary gear limited slip differential of claim 1, it is characterized in that, the first and second non-round central gear structures are identical, and the duplex non-circular planetary gear has three groups and evenly distribute 90 ° of duplex non-circular planetary gear phase phase differences around described non-round central gear.

3. according to claim 1 or 2 described non-circular planetary gear limited slip differentials, it is characterized in that duplex non-circular planetary gear and non-round central gear velocity ratio rule are pressed following formula

Selected, wherein: i ₃₁Be the velocity ratio of duplex non-circular planetary gear and non-round central gear, z ₁, z ₃Be respectively the non-round central gear and the duplex non-circular planetary gear number of teeth,

Be non-round central gear corner, c=0～0.5 is a constant.

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