Differential

FIELD: mechanical engineering.

SUBSTANCE: differential comprises housing (1), cross-shaped or straight shaft (5) of satellites, a number of satellites (4), and gear pair (2) of semiaxles. When gears (2) of semiaxles cooperate with satellites (4) the gear ratio changes at least in two stages. The number of stages is multiple to the number of teeth in satellites (4) and gears (2) of the semiaxles.

EFFECT: expanded functional capabilities.

16 cl, 5 dwg, 1 tbl

 

The technical field

The present invention relates to differentials with limited slip for wheeled vehicles, in particular to the differential with limited slip with changing gear ratio.

Prior art

It is now widely known for the numerous designs of LSD, which in principle can be divided into the differentials of several types, namely: the differential with internal friction overrunning differential, automatic differential lock electronic differential traction control system with electronic control, used in conjunction with pneumatic brake system, differential with the potential barrier. All these differentials have various shortcomings.

Differentials with internal friction, which are the most commonly used model differential with high friction, can be further broken down into pre-loaded differential and pre unloaded differential. The lack of both differentials is the high cost, the latter can be even more costly. The shortcomings of the first of these are relatively large resistance management and CPA is additional rapid tire wear.

Passing the differential has a low reliability, unstable and complex structure.

The disadvantages of automatic differential locking device with electronic control are also the not enough a stable complex structure.

Traction control function represented by the pneumatic brake system has a relatively large power consumption.

In this patent application describes a limited slip differential, which belongs to the differential potential barrier and has such advantages as simple structure, high reliability and suitable traction. These functions are realized through periodic changes of the gear ratio between the satellites and the gear axes. The satellites have an odd number of periods of changing the gear ratio of one revolution, therefore, when the gear ratio between the satellites and one pinion axis reaches its maximum, the gear ratio between the satellites and other gear axis reaches its minimum. Thus, is the unequal distribution of torque to the two gear shafts. If the satellites will turn on half of the period changes of the gear ratio, it will change the distribution of torque on both gears axes. It is periodic and the change in the torque distribution leads to the formation of two potential barriers. If the ratio of the torques acting on the two gear axes, reaches maximum distribution torque, the differential cannot provide continuous differential rotation, thereby limiting the slipping drive wheel. However, still available for products period changes the gear ratio is equal to only one step. For each step should be completed once the relative acceleration and deceleration of the satellite and gear axes, while the relative angular acceleration is relatively large, and its magnitude will be proportional to the range change gear ratios and proportional to the square of the number of periods of changing the gear ratio of one revolution of the satellite. The relatively large relative angular acceleration leads to relatively greater curvature between surfaces of the tooth reduces the permissible load on the gear pair, leads to noise. Although by optimizing available to some extent to increase the range of change of the gear ratio, but the result will be limited. A further increase of the range of change of the gear ratio would have led to a rapid increase in the relative curvature between the surfaces of the teeth and even to the appearance of defects on the surface of the teeth. According to the traditional method of calculating the one-period maximum changing the gear ratio, due to differential movement between the two gear axes is only 1:1,38 for gear pairs with 7 teeth satellite and 12 teeth pinion shafts, and a gear pair having satellites with 9 teeth and gear axes with 12 teeth, it is reduced to 1:1,31 that is still not enough for vehicles intended for use off-road.

The invention

The aim of the present invention is the creation of a limited slip differential, a high range gear ratio and a relatively large coefficient of offset torque, which can significantly increase the throughput, if one of the wheels moves on icy and snow-covered road surface.

To achieve the above purpose, the technical solution according to the present invention is the limited slip differential with variable gear ratio, which periodically changes the gear ratio between the satellites and the gear axes offset torque between the two gear axes becomes a periodic function of the angle of the satellites, so limited to the slipping drive wheel with one hand. The differential includes, mainly, the housing of the differential, to the est or straight shaft satellites, mounted in the housing of the differential, satellites and a couple of the gear axes located in the housing of the differential and siteplease with satellites with the change of the gear ratio and the gear ratio between the satellites and the gear axes is at least two steps; the number of steps in each period corresponds to the total divisor of the number of teeth in the satellites and the gear axes. Each time of changing the gear ratio involves a group of teeth, in which the number of teeth corresponds to the specified number of steps; consolidated operating range of the teeth of each group covers the full range of satellites and gear axes throughout the period of change of gear ratio. For each group of identical gears corresponding teeth have exactly the same implementation.

The operating range for each tooth in each group can be determined in the process of calculation and there is a small overlap of working intervals adjacent gear pairs.

In a preferred embodiment of the present invention specified number of steps equal to 3 and, therefore, the number of teeth as satellites and gear axes is a multiple of 3. Nearby three teeth in one group of teeth are consistently low tooth, high tooth and the other low tooth height, the same is the height of the previously mentioned low tooth, however, there is a shallow depression between the high tooth and low and deep hollow between two low teeth.

In another embodiment of the invention three adjacent teeth in the same group of teeth are consistently high tooth lower tooth and other high tooth height equal to the height of the previously mentioned high tooth, however, there is a deep depression between high and low tooth and a shallow depression between two tall teeth.

The satellites have an odd number of groups of teeth, and when the gear ratio between the satellites and the gear one axis reaches the maximum value, the gear ratio between the satellites and other gear axis reaches a minimum value. The number of groups of teeth on the gear axes is an integer multiple of the number of satellites, so that each satellite operates at the same phase angle.

Mentioned gear ratio is a function that resembles the following:

where Z1- number of teeth on the gear axes, Z2- number of teeth on the satellites(1)- the angle of rotation of the gear axis and(2)- the angle of rotation of the satellites. The range for the number of teeth Z1on the gear axes is 9, 12, 15, 18, and the range for the number of C the tooth tops Z 2on the satellites is 9, 15. The area of values is 0.2-0.4, and the range of values ofrat -of 0.7-1.0.

Low section profile bevel gear pairs with variable gear ratio, that is, below the pole of the line gear, is an analytical curve, and the high part, i.e. on the pole line gear is paired profile the profile of the tooth of the analytical curve, which according to the desired transmission number pointwisely determined on the basis of the principle of engagement, whereby the relative speed between the surfaces of the teeth perpendicular to the normal analytical profile of the tooth at the point. When mated profile is engaged with the analytical profile, the relative movement between the gear pair can satisfy the equation resembles the following:

where Z1- number of teeth on the gear axes, Z2- number of teeth on the satellites(1)- the angle of rotation of the gear axes and(2)- the angle of rotation of the satellites. The area of values is 0.2-0.4, and the range of values ofrat- 0,7-1,0. The range for the number of teeth Z1on the gear axes is 9, 12, 15, 18, and the range of the number of teeth Z2on satellites, 9, 15. Analiticheskii the I curve is a composite curve, consisting of straight lines, arcs, circles, arcs, ellipses, involute and logarithmic spiral. As each pair of teeth in the group has a defined working range, each tooth in the group has a certain shape of the profile.

The essence of the present invention is that the number of steps in the period of change of the gear ratio is increased to two or more, as a result, compared with the traditional method of calculating the number of changes of the gear ratio during a single revolution of the satellite is reduced to the value of one second or less. Thus, simultaneously with the expansion of the range of change of the velocity ratio can significantly reduce the relative angular acceleration between the satellite and the gear axes.

Compared with the prior art the present invention has the following advantages.

The differential according to the present invention is a differential variable gear ratio, the change of the gear ratio is in the process of gearing between the satellite and the gear axes, and the period of the change gear ratio is increased to two steps or more. Thus, the range of change of the gear ratio can be significantly increased while simultaneously the possible reduction of the relative angular acceleration between the satellite and W is starname axes.

In a preferred embodiment, the present invention features a differential with a three-step period of the change gear ratio, and the change of the gear ratio is carried out in the course of the engagement between the satellite and the gear axes, and the period of change of velocity ratio is three steps. As the period of the change gear ratio is increased to three steps, significantly reduced the relative angular acceleration between the satellite and the gear axes, and the ratio of speeds between the gears of the two axes reaches 1:1,85 if still the absence of defects on the surfaces of the teeth. Due to the increase of the range of change of the velocity ratio increases, the potential barrier for the differential rotation; at the same time expanding the range of the rotation angle of the satellites due to the corresponding large coefficient of offset torque; the width of the potential barrier is increased, which reduces the probability of exceeding the potential barrier due to random vibration satellites and increases traction control reliability. Thus, the distribution of torque differential increased significantly.

Brief description of drawings

Figure 1 - schematic view of a differential according to the present invention,

Fig - the image design of the gear shafts according to the present invention,

Figure 3 - image design of a satellite according to the present invention,

Figure 4 - image of the design of the gear axis according to another variant implementation of the present invention,

Figure 5 - image design of a satellite according to another variant implementation of the present invention.

A detailed description of the preferred options

for carrying out the invention

Below is more detailed description of the present invention in combination with the variants of the implementation and drawings.

Option 1

Figure 1-3 shows a design variant of the implementation according to the present invention. Limited slip differential with variable gear ratio, proposed according to the present invention, includes a housing 1 differential, shaft 5 satellites, made a Phillips or straight and located in the housing 1 differential, satellites 4 and a pair of gears 2 axes, spherical thrust bearings 6, located between the rear surface of the satellites 4 and housing 1 differential, flat thrust bearings 3, located between the rear surface of the gear 2 axes and housing 1 differential. These satellites 4 and gears 2 axes form a multiple gear pairs.

In the embodiment 1 of implementation of the present invention, the number of teeth as satellites 4 and gears 2 axes selected multiple of 3. In the process of gearing gear ratio is changed with a period containing three steps. Thus, in each period changes gear ratios involved a group of three adjacent teeth, each of which has a specific profile. In the group of three teeth each has a certain operating range, because the height of the teeth in the group is different, and each has an individual profile.

On the same gear corresponding teeth of the same group have the same profile and the same height. The satellites 4 has odd number of groups of teeth, which achieves the maximum value of the gear ratio between the satellites 4 and gears 2 one axis and the minimum value of the gear ratio between the satellites 4 and gears 2 the other axis, thus, allows to reach the maximum coefficient bias torque between the two gear axes. The number of groups of teeth on the gears 2 axes is a multiple of the number of satellites 4, which provides each satellite 4 at the same phase angle. This avoids the kinematic mutual influence between the satellites 4 and gears 2 axes.

This variations is the implementation of the present invention, the range of selected values of the number of teeth in gears 2 axes is 9, 12, 15 and 18, and the range of the number of teeth on the satellites 4 is 9 and 15. Mentioned three teeth, forming one group, are consistently as low tooth, high tooth and the other low tooth, which has the same height with the mentioned low tooth. For gears 2 axes between the high tooth 7 and low tooth 8 has a shallow trench 9, and between the two lower teeth 8 - deep trench 10. In the satellite 4 has a shallow depression between 12 high 13 tooth and lower tooth 14 and the deep trench 11 between the two lower teeth 14.

In this embodiment of the invention, the period of the change gear ratio is increased to three steps, as a result, compared with the traditional method of calculating the time of changing the gear ratio of one revolution of the satellite is reduced to one third, so that along with the considerable expansion of the range of change of the velocity ratio may be reduced relative angular acceleration between the satellite and the gear axes. Therefore, achieving the goal of the present invention.

The change of the gear ratio is a function that resembles the following:

where(1)- the angle of rotation of the gear axes,(2)- the angle of rotation of the satellites. In a preferred embodiment, blast values is 0.2-0.4, the area values ofrat -0.7 to 1.0, and the attitude change of speed between the two gear axes is approximately 0.5 to 2.0.

The calculation of the tooth profile is based on fulfilment of the above according to the gear ratio. Having these profiles on a single element gear pairs, the profiles of the other element can be determined point by point in accordance with theorem gearing, whereby the relative speed between the side surfaces of the teeth should be perpendicular to the normal of the above specified profile of the tooth at the point. However, you must ensure that all the profiles are represented by convex curves, each tooth had a corresponding width of the head and width of the legs, and there was a corresponding overlap between adjacent pairs of teeth. The method of calculation of the tooth profile according to the present invention is based on the fact that the lower part of the profile, that is, below the pole line, is a simple analytic curve, which is a combination of straight lines and arcs of a circle and an ellipse, while the upper part, i.e. above the pole line is paired analytical profile curve, which is determined by a point-by-point, on the basis of theorem gearing, whereby the relative speed between the side surfaces of the teeth perpendicular to the normal the analytical profile of the tooth at the point.

Some of the parameters and the experimental data of embodiments according to the variant 1 below:

ExamplesZ1Z2CratThe range of change of the velocity ratio between the gear axesThe distribution of torque
11290,3-0,32of 0.9 to 0.920,515-1,9414,5-6,9
21290,28-0,30,86-0,880,538-sm 1,8573,5-4,7
318150.18 to 0.20,93-0,950,667-1,5002,7-3,0

The parameters and the experimental data shown above are to illustrate the invention but do not limit the present invention.

Through a rational choice of the number of teeth in the satellites and the gear axes, 3 times, the period of the velocity ratio will becalculated as equal to three steps.

In this embodiment of the invention a periodic variation in the velocity ratio between the two gear axes is used to create potential barriers differential rotation and only the about in that case when the difference in the torques applied to the two gear axes will exceed the potential barrier of differential rotation and friction torque, gear differential will be able to overcome a potential barrier to provide continuous differential rotation. Otherwise, gear differential will only be able to fluctuate within the same period of the change of velocity ratio, i.e. three steps. Option 2

In figures 1, 4 and 5 show a second variant implementation of the present invention.

In this embodiment of the invention the design of the differential, it is a principle of action and result are the same as in embodiment 1, and therefore will not be again described in detail.

In figures 1, 4 and 5 shows the design according to this variant embodiment of the invention. According to the present invention, the limited slip differential with variable gear ratio contains the differential housing 1, the shaft 5 satellites, made a Phillips or straight and located in the housing 1 differential, 4 satellites and a couple of gears 2 axes, spherical thrust bearings 6, located between the rear surface of the satellites 4 and housing 1 differential, flat thrust bearings 3, located between the rear surface of the gear 2 axes and housing 1 differential. These satelli the s 4 and gears 2 axes form a multiple gear pairs.

In this embodiment of the invention, the number of teeth and satellites 4 and gears 2 axes selected multiple of 3. In the process of gearing gear ratio is changed with a period containing three steps. Thus, in each period changes gear ratios involved a group of three adjacent gear pairs, each of which has an individual profile. As in the same group each of the three teeth has an individual range of each tooth in the group has an individual profile and height. On the same gear corresponding teeth of the same group have the same shape and height. The satellites have an odd number of groups of teeth, and the number of groups of teeth on the gear axes is a multiple of the number of satellites.

The difference between this option and the above of the embodiment of the invention is that in these groups of three teeth adjacent teeth are consistently high tooth lower tooth and high tooth height equal to the height of the previously mentioned high tooth. On the gear 2 axis there is a deep cavity 24 between the high tooth 21 and a lower tooth 22 and a shallow cavity 23 between two tall teeth 21. On the satellite 4 features a deep cavity 28 between the high tooth 25 and low tooth 26 and a shallow cavity 27 between the high teeth 25.

It is the embodiment of the invention, the operating principle is identical with the foregoing. Period changes of velocity ratio increased to three steps, as a result, compared with the traditional methods of calculating the time change of the velocity ratio for one revolution of the satellites 4 is reduced to one third. Thus, simultaneously with the expansion of the range of change of the velocity ratio can significantly reduce the relative angular acceleration between the satellite 4 and gears 2 axes.

The principle of operation and method of calculation for option 2 implementation is identical to option 1 implementation and are not described again.

The above figures and description of option 2 implementation is used for the disclosure of the invention, but not limit it.

1. Differential variable gear ratio and limited slip, in which the ratio of the bias torque between the two gear axes is a periodic function of the angle of the satellites with limited slippage of one of the wheels, the differential includes a differential case, a Phillips or straight shaft satellites installed in the housing of the differential, a lot of satellites mounted on the shaft of the satellites, the pair of gears of the mechanism located in the housing of the differential interactions with satellites, while the gear axes and satellites made from vozmojnostiami at the specified interaction of the gear ratio between the satellites and the gear axes with period comprising at least two steps, and the number of steps in the period corresponds to the total divisor of the number of teeth of the satellites and gear axes and gear axes and satellites are designed to match the numbers involved in each period of the teeth to the number of steps of the period; and gear axes and satellites made with the possibility of engaging in each age group of teeth and the number involved in each period of the teeth corresponds to the number of steps of the period, consolidated operating range of the teeth of each group covers the full operating range of the period and for each group of teeth of one gear corresponding teeth have the same design.

2. The differential according to claim 1, in which the defined operating range for each pair of teeth in each group and there is a small overlap of the operating range between adjacent pairs of teeth.

3. The differential according to claim 1, in which the number of teeth of the satellites and gear axes is divisible by 3, and in the interaction of the gear ratio change during 3 times.

4. The differential according to claim 1, the satellite has an odd number of groups of teeth, and when reaching the ratio between the satellites and the gear one-half-maximum gear ratio between the satellites and other gear axis is minimal.

5. The differential on P1, in which the number of groups of teeth on the gear axes divisible by the number of satellites with each satellite in the same phase angle.

6. The differential according to claim 3, in which each group of teeth consistently contains low tooth, high tooth and lower tooth height equal to the height of the low tooth, between high tooth and lower tooth has a shallow depression, and between the two low-teeth - deep trench.

7. The differential according to claim 3, in which each group of teeth consistently contains a high tooth lower tooth and high tooth height equal to the height of the high tooth, between high tooth and lower tooth has a deep cavity, and between the two high-teeth - shallow trench.

8. The differential according to claim 3, in which the gear ratio between the gear axes and satellites is a function that resembles the following:

where Z1- number of teeth on the gear axes, Z2- number of teeth on the satellites, φ(1)- the angle of rotation of the gear axes, φ(2)- the angle of rotation of the satellites.

9. The differential of claim 8, in which the range of the number of teeth for gear Z1axis is 9, 12, 15, 18, and the corresponding range of the number of teeth for the satellite Z2is 9, 15.

10. The differential of claim 8, where the values area Sostavljaet of 0.2-0.4.

11. The differential of claim 8, where the values area of the rat is 0.7 to 1.0.

12. The differential according to claim 1, in which the profiles of the lower parts of the teeth on the satellites and the gear axes, i.e. below the pole of the line gear, are analytic curves, and the upper part of the teeth are paired profiles to the profiles of the analytical curve of the teeth, which is defined point-by-point, on the basis of theorem gearing, whereby the relative speed between the side surfaces of the teeth perpendicular to the normal analytical profile of the tooth at the point.

13. Differential indicated in paragraph 12, in which when paired profiles in contact with the analytical profiles agreed teeth gear ratio satisfies the following equation:

where Z1- number of teeth on the gear axes, Z2- number of teeth on the satellites, φ(1)- the angle of rotation of the gear axes, φ(2)- the angle of rotation of the satellites.

14. The differential in item 13, in which the area of values is 0.2-0.4, and the range of values of rat - 0,7-1,0.

15. The differential in item 13, in which the range of the number of teeth on the gears Z1axes is 9, 12, 15, 18, and the range of the number of teeth on the satellites Z2is 9, 15.

16. Differential indicated in paragraph 12, in which the analytical curve is predstavljaet a combination of a straight line, arcs of circles and arcs of an ellipse.

17. Differential indicated in paragraph 12, in which all profiles are convex curves.



 

Same patents:

FIELD: transport engineering.

SUBSTANCE: proposed differential has case 1 which accommodates coaxially installed axle-shafts of drive wheels, cages 7, 8, driven bushings 3, 4 with splines for connection with drive wheel axle-shafts coaxially installed in cages. Case 1 is made in form of cylindrical bushing on inner surface of which longitudinal wedging cavities for rollers 5, 6 are made. Each roller in each cavity can move along driven bushing from one wedging position into the other. Cages 7, 8 are made in form of hollow cylinders with rectangular holes on surface whose number corresponds to number of longitudinal wedging cavities for rollers. On end face surface of cages 7, 8 at least one slot is made on end face surface of one cage and hole with rigidly fitted-in pin on end face surface of other cage. Pin of one cage gets into slot of other cage forming movable link for angular displacement of cages in relatively opposite directions.

EFFECT: improved reliability, roadability and safety of vehicle.

5 dwg

The invention relates to the field of engineering, in particular to driving axles for cars and motorcycles supplied by the differential mechanisms to ensure non-rigid kinematic connection between the two wheels of the axle

The invention relates to transport machinery and can be used in a four-wheel drive

The invention relates to the transport industry, in particular to the structure of the cross-axle differential mechanisms

The invention relates to the automotive industry and can be used, in particular, in the automobile and minigroove cars

The invention relates to the field of engineering

The invention relates to vehicles, particularly to a differential mechanisms

The invention relates to mechanical engineering and can be used in vehicles terrain

The invention relates to the field of mashinostroenia and can be used in vehicles terrain

Differential drive // 2162973
The invention relates to the field of engineering, in particular to actuators

FIELD: transport engineering.

SUBSTANCE: proposed differential has case 1 which accommodates coaxially installed axle-shafts of drive wheels, cages 7, 8, driven bushings 3, 4 with splines for connection with drive wheel axle-shafts coaxially installed in cages. Case 1 is made in form of cylindrical bushing on inner surface of which longitudinal wedging cavities for rollers 5, 6 are made. Each roller in each cavity can move along driven bushing from one wedging position into the other. Cages 7, 8 are made in form of hollow cylinders with rectangular holes on surface whose number corresponds to number of longitudinal wedging cavities for rollers. On end face surface of cages 7, 8 at least one slot is made on end face surface of one cage and hole with rigidly fitted-in pin on end face surface of other cage. Pin of one cage gets into slot of other cage forming movable link for angular displacement of cages in relatively opposite directions.

EFFECT: improved reliability, roadability and safety of vehicle.

5 dwg

Differential // 2267676

FIELD: mechanical engineering.

SUBSTANCE: differential comprises housing (1), cross-shaped or straight shaft (5) of satellites, a number of satellites (4), and gear pair (2) of semiaxles. When gears (2) of semiaxles cooperate with satellites (4) the gear ratio changes at least in two stages. The number of stages is multiple to the number of teeth in satellites (4) and gears (2) of the semiaxles.

EFFECT: expanded functional capabilities.

16 cl, 5 dwg, 1 tbl

Muscular drive // 2270780

FIELD: transport engineering; bicycles.

SUBSTANCE: invention is designed for devices automatically changing gear ratio without interruption of power flow. Proposed drive contains two differentials. Force sensor 5 is installed between input shaft 8 and common input of both differentials, namely power differential 1 and regulating second differential 2. Said force sensor 5 cuts in braking device 4 at rise of load, said braking devices is idling at direct drive and is connected with regulating input of second differential 2. As a result, output gear 21 of second differential 2 starts rotating and self-braking drive 3 releases carrier 25 of power differential 1. Proposed drive automatically changes over from direct drive to drive with changed gear ratio. Moment of changing over can be regulated by tensioner 6 of spring 19 of force sensor.

EFFECT: facilitated selection of step-down gear in wide range of gear ration depending on individual capabilities of user.

1 dwg

FIELD: mechanical engineering.

SUBSTANCE: invention relates to methods of control of differential locking of multidrive wheeled vehicles and it can be used at designing of systems to control tractive forces of driving wheels of multidrive vehicles and carrying out investigations of wheeled vehicles. proposed method of control of differential locks comes to locking of differential for definite periods of time at threshold values of mismatching of mechanical parameters of driving wheels intercoupled by said differential and unlocking differential at expiration of definite of time or at achievement of threshold value of steerability index. Unlocking of differentials at achievement of threshold value of steerability index is carried out individually, starting from differential whose locking has greater effect on steerability of wheeled vehicle.

EFFECT: enlarged range of control of traction forces on driving wheels to increase cross-country capacity and traction and speed properties at provision of required steerability of multidrive wheeled vehicles.

1 dwg

FIELD: transport engineering.

SUBSTANCE: invention can be used to increase cross-country capacity and stability of vehicle at braking. Proposed differential lock mechanism contains locking device in form of friction mechanism including two members 1 and 2. Friction mechanism consists of pack of friction disk 3 and steel disks 4, two control pistons 7, air feed head 8 with union 9. Members 1, 2 of clocking device are connected by pairs of gears 10, 11, 12, 13 with axle-shafts 14, 15. Device is furnished additionally with air fed control system consisting of angular velocity pickups 16, 17, electronic control unit 18, electromagnetic control valve 19, relief valve 20, change-over switch 21, connecting air lines and electric wires.

EFFECT: increased cross-country capacity and stability of vehicle.

2 dwg

FIELD: mechanical engineering; vehicle transmissions.

SUBSTANCE: proposed differential contains case 1, side gears 2, and 3, planet pinions and locking device. Locking devices is made in form of ring shifter 7 connected with drive 8, pushers 10 arranged inside axles 9 of planet pinions, intermediate members and locking members. Differential includes also elastic stop, and spring inserts 17 and 18 placed between case 1 and rear surfaces 20 and 21 of side gears 2 and 3. Grooves are made on end face front surfaces of side gears 2 and 3. Said grooves have wavy profile corresponding to profile of locking members, and number of radial grooves is even.

EFFECT: prevention of failure of differential lock caused by wedging of locking members between side gears, and falling out of locking members at unlocking, provision of stepless row of values of locking coefficient.

5 cl, 6 dwg

FIELD: automotive industry.

SUBSTANCE: invention can be used in differential drives of wheeled vehicles made for automatic locking of wheels. Proposed self-locking differential of vehicle contains drive case 1 accommodating axle shaft-members 4, 5 arranged coaxially to each other and coupled with axle-shafts 2, 3. Said axle-shaft members are provided with helical grooves 6, 7 on outer surface with opposite hand of helix, solids of revolution in form of balls 8 filling in line at least one closed channel 10 made in drive case. Part of said channel is opened to dip segments of balls into helical grooves. Closed channel 10 is made rectangular in longitudinal section, with rounded off outer angles 12. Cross section of legs of rectangular closed channel is equal to diameter of balls 8. Number of balls in channel is odd.

EFFECT: simplified design of differential, reduced overall dimensions, increased manufacturability, strength and efficiency at self-locking.

4 dwg

FIELD: transport engineering; vehicle transmissions.

SUBSTANCE: invention can be used in differential drives of vehicles with possibility of automatic wheel locking. Proposed self-locking differential of vehicle contains drive case accommodating axle-shaft members coupled with axle shafts and provided on outer surface semi-round in cross section screw grooves of opposite hand of helix, solids of revolution in form of balls filling, in chain, closed channels made in drive case and containing working grooves opened to dip ball segments into screws of axle-shaft members, longitudinal bypass channels and side return channels. Inner part of case consists of three parts. On extreme parts working grooves are made with opposite direction of helix relative to each other and to screw grooves of axle-shaft members. Middle part is made with width not exceeding diameter of balls and is furnished with through axial holes corresponding to size of diameter of balls. Angle of tilting of working and screw grooves to longitudinal axis is 74-76°. Side return channels in longitudinal section are made with sizes steplessly increasing from diameter of ball on ends of channels to 1.5 diameter of ball in central part of channels. Longitudinal bypass channels in cross section are made to size of diameter of ball, and inner side of channels is made at angle of 1-2° to center of bypass channel, with stepless transition in place of connection.

EFFECT: improved reliability and efficiency of locking.

4 cl, 3 dwg

FIELD: mechanic.

SUBSTANCE: the self-blocking differential contains a power-driven shell with lids, in which half shaft elements are placed coaxially and connected with the half shaft. The half shaft elements, on their upper surface, have spiral channels running in a direction opposite the spiral, odd number of rolling elements (balls), one closed channel containing a working groove open for inserting ball segments into the spiral channels of the half shaft elements; a longitudinal return channel with dimensions equal to the ball diameter, connected by intermediate channels made in the lids of the power-driven shell. The outside surface of the intermediate channels in the longitudinal section has a radius equal to 1.25 diameters of the ball; and their wall, at the outlet to the zone of connection to the return channel, contains a straight section. In the lids, a slot with dimensions equal to those of the working groove is made for placement of spiral channels of the half shaft elements in the intermediate channels area.

EFFECT: increased reliability of self-blocking differential.

4 cl, 2 dwg

FIELD: mechanic.

SUBSTANCE: the self-blocking differential contains a power-driven shell with lids, in which half shaft elements are placed coaxially and connected with the half shaft. The half shaft elements, on their external surface, have spiral grooves with a semi-circular cross-section, the direction of which is reverse to that of the spiral, rolling elements (balls) filling the closed channels in the power-driven shell, in chains. The closed channels contain working grooves open for inserting ball segments into the spiral grooves. The longitudinal bypass channels and the side return channels are formed by slots in the lids and cuts around the perimeter of the distribution washers installed on the half shaft elements. The distribution washers have a diameter equal to the working groove dimension.

EFFECT: increases reliability of self-blocking differential.

2 cl, 1 dwg

Up!