WO1987006668A1

WO1987006668A1 - Self-locking differential for motor vehicles

Info

Publication number: WO1987006668A1
Application number: PCT/CH1986/000060
Authority: WO
Inventors: Josef KÖPFLI
Original assignee: Koepfli Josef
Priority date: 1986-05-01
Filing date: 1986-05-01
Publication date: 1987-11-05

Abstract

In the self-locking differential a hydraulic pump/motor system (21 - 28) is connected between at least one of the axle shafts (1, 3) and the differential housing (7). This system comprises gear wheels (21) rotatably mounted in radial flanges (15) of the differential housing (7) at a radial distance from the axle shaft (3), said gear wheels being engaged with one freely rotatably gear wheel (22) arranged coaxially on the axle shaft (3) and, with the aid of a hydraulic gear wheel pump, pumping the oil present in the differential housing from one pair of gear wheels (21, 22) to the next pair of gear wheels (21, 22) in a peripheral direction via connecting ducts (24, 25). Four peripherally distributed gear wheel pairs (21, 22) are connected with one another by four connecting ducts (24, 25). These connecting ducts (24, 25) contain shut-off devices (26, 27) in the form of ball-valves, which shut off the connecting ducts when a certain oil speed is attained. The differential housing (7) is then connected via the no longer rotatable gear wheels (21, 22) with the axle shaft (3) and as a result the differential operation is inhibited.

Description

for motor vehicles, with a rotating ahtre. bb ren differenti al orb, in this differential gear wheels rotatably mounted on the differential axles and with these meshing gear teeth arranged on the two axle shafts.

Self-locking differentials have the task _to, verhi change that the engine torque flow to _the, drive wheel with the lower grip, as it is in a normal differential without lock the case, which then, for example, with the result that, for a one-sided poor grip the torque from the slipping wheel can not be recorded and thus the other wheel can not transmit torque. If the inside wheel of a powerful vehicle is relieved when cornering, this wheel also tends to spin and can lose grip due to jumping, and if the wheel grips again and the torque increases backwards, the vehicle can easily skid devices.

To avoid these disadvantages that are inherent in normal differentials, differential brakes and differential locks are used, which are used particularly in vehicles that move away from roads, such as construction machines and tractors, etc., because the grip of the drive wheels on these vehicles is often very different.

Various differential brakes and self-locking ^' ifferentials are known, with the help of from between. ^' The Differi al basket and the machine elements acting axle shafts a relative rotation of the axle shafts to the differential basket is difficult. These machine elements consist, for example, of worm wheels arranged in the differential cage-mounted shaft pairs, one of which is in engagement with a worm arranged on an axle shaft, in such a way that the worm wheels lock the worms and the axle shafts are thereby set in rotation. The almost self-locking worm gear enables roll compensation when cornering.

Another possibility to complicate a Relati rotation of the axle shafts to the Differi al basket is the arrangement used in a known limited slip differential for each arrangement of a multi-disc brake between the axle shafts and the Differenti al basket, the Aussenl amel len torsionally with the Differi al basket and the inner plates are connected to the bevel gears in a torsion-proof manner. It is also already known to connect a differential to a viscose clutch, in which the property of a viscous liquid such as silicone is used to change the flow behavior depending on pressure and temperature. With this clutch, the viscous fluid is located in a cylinder in which disk wheels rotate. The lamellae have slots and holes and if a difference in the number of revolutions occurs, the slower lamellar wheel is taken along by the faster lamellar wheel due to the shear forces, the effect of the shear forces increasing with increasing speed difference, whereby heating occurs, as a result of which the air present distributed as small bubbles in the liquid and this liquid becomes almost solid in extreme cases. The disadvantage of this viscose coupling is the heat dependency, because after an increase in shear forces caused by heating up to complete blocking in extreme cases, cooling for the normal operating state also occurs again.

Differential brakes with worm gears on the differential make the drive system noticeably more expensive and are therefore mainly found in expensive vehicles. With other constructions such as the multi-plate clutches integrated in the differential, wear must be expected.

The present invention was therefore based on the object to create a Sel limited slip differential, which requires few and inexpensive to produce additional elements to the actual differential, which does not affect the Rol 1 compensation when cornering 'and the Differi alwi effect only from one before ¬ abolishes limit value and works elastic. This is achieved according to the invention by a hydraulic pump / motor system interposed between at least one of the two axle shafts and the differenti al basket, with displacement bodies working as a pump or motor, the working spaces of which are connected to one another by a flow circuit for the hydraulic medium, wherein in throttling or shut-off devices are arranged in the connecting lines, which throttle or shut off the delivery flow of the pump / motor system which only occurs when a relative rotation between the axle shaft and the differential basket occurs when a definable limit value is exceeded, as a result of which as a result, the rotation-locked or rotation-locked pump / motor system brings about an at least approximately loss-free torque transmission between the differential or axle and the axle shaft. The hydraulic pump / motor system, which is only present on one axle shaft, represents the simplest embodiment in which the torque is transmitted to the second axle shaft via the differential gears which are constantly in engagement with the axle gears. In the most common embodiment of the differential, the axle gears arranged on the axle shafts and the differential gears mounted on the differential axles are bevel gears, via which the torque is transmitted from one side to the other as soon as a relative rotation occurs between the axle shaft and the differenti al basket driven by the motor, the pump / motor system that is starting to work at this moment is blocked by closing the shut-off elements in the connecting lines depending on the flow speed, as a result of which the differential effect is eliminated.

The engine torque can be transferred to both axle shafts even more effectively if, in a further embodiment of the self-locking differential between each of the two axle shafts and the differential basket, a hydraulic pump / motor system divided between the two axle shaft sides also works as a pump or as a motor the displacement bodies is interposed. One has then a ^'endurance of both Achswel enseiten symmetrical same arrangement with the result of a direct rotary momentüb of the differential cage on each of the two axle shafts. The torque then no longer has to go through the differential bevel gears from one side to the other having the motor / pump system Axle shaft are transmitted.

Various exemplary embodiments of the invention are explained in more detail below with reference to the drawings, in which: Fig. 1 shows an axial section through a first

Embodiment ■ 'des, Seil.tbsItsperrdiffe ^ι r.e1ntiaJls;

Fig. 2 'a''| UιersII! CLhni t after dIerl.lLi ^l n ^? ie 2-2

¹ l 'ij in Fig. 1 by a töil of the Differrentj.ialkorbes without the displacement body contained therein; 3 shows a section through the part shown in FIG. 2 along the line 3-3; ^! _j .

. Fig. 4 is a section through the dargje in Figure 2 is ¹⁴ - set part along the line 4-4;

Fig. 5 shows an axial section through another embodiment of the limited slip differential. I both sides of the axle shaft symmetrically arranged displacement bodies of the hydraulic pump / motor system;

6 shows a cross section along the line 6-6 in Figure 5 through the differential carrier. 7 shows a cross section along the line 7-7 in FIG. 5 through the differential cage;

8 shows an axial section through a further embodiment, with the exception of the gear ratio as in FIG. 5; 9 shows an axial section through a further embodiment, without a gear ratio and otherwise the same as FIG. 5;

10 shows the embodiment according to FIG. 9 with an additional axial piston pump; Fig. ' 11 shows an axial section through a further embodiment, with a differential cage divided into two housings;

12 shows an axial section through an embodiment as a planetary distributor differential. 1 has a left axle shaft 1 with an axially bevel gear 2 which is arranged in a rotationally fixed manner at the end and also a right axle shaft 3 with an axially bevel gear 4 which is arranged in a rotationally fixed manner at the end. The two axle bevel gears 2 and 4 are in engagement with a plurality of differential bevel gears 5, of which only one differential bevel gear 5 is shown in FIG. 1, which is rotatably mounted on a differenti al axis 6, which is held in basket 7 in di fferenti al. The differenti al basket 7 represents a housing enclosing the acJis bevel gears 2 and 4 and all the differenti al bevel gears 5, which is filled with oil up to about the central axis of the axle shafts 1 and 2. On the differential cage 7, the ring gear 8 is screwed onto one end face, which is driven by the vehicle engine by means of gear means, not shown in the drawing.

The Differenti al basket 7 with the ring gear 8 ^■ is rotatably mounted in an outer housing 11 via a left roller bearing 9 and a right roller bearing 10. An Achstrom¬ pete 12 are screwed to this housing 11 on both sides. The outer housing 11 is filled with the hydraulic medium, which preferably consists of oil, up to approximately the center of the axis of the axle shafts 1 and 2. The differenti al basket 7 comprises a radial flange 14 forming the right end surface and an inner radial flange 15 and an annular part 1 16 arranged between them, which is shown in cross section in FIG. 2. The radial flanges 14 and 15 and the annular part 16 arranged therebetween are screwed together on a subsequent cylindrical part 17 of the differential cage 7 by means of a plurality of continuous screws 18, all of which Parts 14, 15, 15 and 17 together form the Differenti al basket 7. The screw holes 19 in the annular part 16 can be seen in Fig. 2.

At a radial distance from the axle shaft 3, five rotary axes are circumferentially distributed in the radial flanges 14 and 15 at equal angular distances from one another

20 rotatably mounted, each carrying a displacement body in the form of a spur gear 21. Another spur gear 22 is coaxial to the axle shaft 3

10 freely rotatable. This spur gear 22 forms, together with a spur gear 21 arranged at a radial distance from the axle shaft 3, a hydraulic pump or a hydraulic motor. In order to multiply the effect, four spur gears are in the example shown

15 21 arranged at a radial distance from the axle shaft 3, all of which are simultaneously engaged with the spur gear arranged on the axle shaft. The spur gears

21 are received in bores 23 in the annular part 16. These bores recognizable in FIG. 2

20 23 form the work spaces for the pump / motor system. From each hole 23 leads to the next following hole 23 in the circumferential direction, cut off a channel

24 and 25 existing channel for the hydraulic medium, this channel 24, 25 extending from an axially

25 den- channel section 24 and from this to adjacent bores 22 radially extending channel sections

25 exists. These channel sections 25 open into the engagement area of the spur gears 21 and 22. The channel section 24, which extends in the axial direction, is one

30 stepped bore, creating two valve seats

26 are formed, against which a ball 27 is pressed as a shut-off device (FIG. 1) around the channel.

24, 25 to shut off. Is located between the two balls 27 8 is a compression spring that holds the two balls 27 in the open position. Depending on the direction of rotation of the spur gears 21 and 22, a ball 27 closes the channel 24, 25 when the flow rate of the oil exceeds a certain value. Instead of the shut-off devices, only throttles in the form of a cross-sectional constriction of the channel could also be provided at this point, which is not shown in the drawings. The section in Fig. 2 over the axially extending channel

10 24 in the radial direction up to the outer edge of the ring-shaped part 16 extending portions of the radially extending channel sections 25 serve only for the production of the channel and are closed at 29 on the outer edge. The interaction of the radial

_First 5 Distance from the axle shaft 3 arranged four spur gears 21 with the spur gear 22 which is arranged coaxially to the axle shaft 3 and which rotates freely on the axle shaft 3 can also be seen from the cross sections according to FIGS. 6 and 7, only the flow channels for the

20 oils are different.

In the working space or the bore 23 for receiving the spur gears 21 also opens an intake duct 30, which is in a shooting position via an automatic intake and by the action of a spring 31

25 held ball valve 32 is in communication with a chamber 33 outside the differential cage 7. From this chamber 33 filled with oil, oil is refilled into the system by suction, so that the system always works reliably and is suitable for the type of gearwheel used here.

30 pumps always occurring leakage loss is compensated. The oil enters this chamber 33 through a scraper 34, which strips off the oil adhering to the differenti al basket 7 circulating in the oil bath at the outside and guides it into the chamber 33. Each of the spur gears 21 arranged in the annular part 16 is in engagement with the spur gear 22 arranged coaxially on the axle 3 and forms by interaction with this spur gear 5

Vehicle is not on, but for example when 10 slips through a vehicle wheel. To determine the effect of the pump to increase still, _[is provided still a translation gear in the embodiment according to FIG. 1. For this purpose, each axis of rotation 20 carries the spur gear

21 inward from the inner radial flange 15 a gear 15 35 ,. which is in engagement with a further gear 36, which is arranged on the axle shaft 3 in a rotationally fixed manner. In the exemplary embodiment according to FIG. 1, this gear 36 is an external ring gear 36 formed on the axle bevel gear 4. The diameter of this ring gear 36 is greater than 0 than the diameter of the spur gear wheel 22, which is one

Quick translation is achieved. The spur gear

22 must therefore be freely rotatable on the axle shaft 3.

A simpler embodiment without translation can be achieved with a spur gear 22 which is arranged on the axle shaft 3 in a manner fixed against relative rotation. Such an embodiment without a translation is shown in FIGS. 9 and 10.

The self-locking differential works as follows:

If one drive wheel of the vehicle has good grip and the other drive wheel has poor grip, the latter drive wheel begins to spin. At this moment there is a relative rotation between the differential cage 7 and the axle shafts 1 and 3. 10

It does not matter whether the axle shaft 1 or the axle shaft 3 spins and the other does not turn due to the better grip, because in any case compared to the driven differential cage 7 a Rel ati vdrehurig

5 occurs. As a result, the radial

Distance from the axle shaft 3 arranged spur gears 21 begin to rotate about its axis and thereby a delivery flow begins in the hydraulic pump / motor system, the oil of which together as a pump

10 working gears 21 and 22 through the channel sections 24 and 25 of the connecting channel to the next following pair of gears in the circumferential direction, which consists of the spur gear 21 and the same coaxially arranged on the axle shaft spur gear 22. Each

15 of the four gearwheel pairs pumps oil through the channel sections to the next gearwheel pairing. However, when the oil reaches a certain flow rate, this flow is stopped by closing the valve seat 26 and the ball 27

20 shut-off device in the channel section 24 interrupted. At this moment, the spur gears 21 can no longer rotate about their axis, and since the axis of rotation 20 of each of the four gears 21 is supported in the differenti al basket 7 and on all four axes of rotation 20

25 arranged gears 35 with the ring gear "36 on the axle bevel gear 4, the torque coming from the engine is transmitted via the differential basket 7 and the aforementioned meshing gears 35 and, 36 to the axle shaft 3. Through the selection -30 the strength of the spring 28 against the valve ball

27 presses, it can be determined at which flow rate the valve is to close. Instead of the valve, a throttle element can also be provided at this point, which throttles the oil flow when a other behavior is desired.

Since the two axle bevel gears 2 and 4 are in mesh with the differential bevel gears 5, the torque is transmitted from one axle shaft to the other Αchswel le via these bevel gears, regardless of which side the drive wheel with the poorer traction is. If, for example, the vehicle wheel connected to the right axle shaft 3 according to FIG. 1 rotates and after closing the shut-off elements in the form of the ball valves 26, 27 the gear wheels .21, 22 can no longer convey oil, the torque via the bevel gears 2, 4 and 5 to the axle shaft 1 with the vehicle wheel which has better traction. A better effect with regard to the transmission of the torque is obtained, however, with an embodiment of the limited-slip differential according to FIG. System interposed. Parts of the limited-slip differential which correspond to the first embodiment are denoted by the same reference numerals in FIGS. 5, 6 and 7. The difference is that in the differenti al basket 7a an annular part 16a with the holes 23 for receiving the gears 21 is arranged on each of the two sides. On each side four gears 21 work together with a gear 22 arranged axially to the axle shaft 1 or 3 and work as a pump or as a motor. The working spaces of the pumps on one side are connected to the working spaces via connecting channels 40 which extend as axially parallel bores through the differential cage 7a of the pumps on the other side. Each connecting channel 40 extends on both sides into the inner radial flange 15, in which the four gear wheels 21 are rotatably mounted, and runs within this radial flange 15 as a radially extending channel section 41 as far as the engagement area of the spur gears 21 and 22 In each of the connecting channels 40 extending in the axial direction through the differential basket 7a there is a shut-off element in the form of a ball valve with a ball 27. and two valve seats 26 so that this ball valve is effective in both flow directions. A spring 28 located on each side of the ball holds the ball valve in the open position. As can be seen from the cross-sectional figures 6 and 7, which also contain the gearwheels 21 and 22, each gearwheel 21, which, together with the gearwheel 22 common to all of them, forms a pump or a motor, is assigned two connecting channels 40, which are connected extend from one side to the opposite side of the differenti al basket 7a, and with the radially extending channel section 41 open into the engagement area of the gearwheels. A shut-off device 26, 27 is present in all eight existing connecting channels 40.

If the left and right vehicle wheels of the vehicle have uneven grip and, for example, a vehicle wheel wants to slip, on this side the gear pumps consisting of the gear wheels 21 and 22 start to pump the oil through the assigned connecting channels -40 to the other side, where the gears 21 and 22 ^'work as a motor, but in turn the oil back through the assigned second connection Pump channel 40 to the other side, since there is a closed circuit between all working spaces of the gears and the connecting channels. This runs ngs-

it-

¹ axes of rotation arranged gears 35, which rπit ^' one

Internal ring gear 42 on the bevel gear 2 or the bevel gear

4 are engaged, is transmitted to this axle bevel gear. With the internal ring gear 42 differs

15 the formation of the axle bevel gear 2 or 4 is still of the embodiment according to FIG. 1, in which there is an external ring gear 36. With the inner tooth 42, a larger transmission ratio is achieved in order to bring about a faster response of the lock. 5 has the advantage that the locking on both axle shafts takes effect immediately and not, as in the embodiment according to FIG. 1, the torque via the differential bevel gears

5 must be transferred to the other side.

It can be seen from FIGS. 6 and 7 that the gearwheels 21 in one annular part 16a are arranged offset by 45 ° to the gearwheels 21 in the other annular part 16a, so that the straight-line connecting channels 40 between them are in each case on the one respectively.

30 on the other side open into the meshing area of the gears. 6 and 7, the total of eight screws 18 can be seen, with which the parts of the differenti al basket 7a are screwed together on the left and on the right side. A further embodiment of the limited-slip differential shown in FIG. 8 differs from the embodiment according to FIG. 5 only in the configuration of the transmission gear between each of the axle bevel gears 2 and 4 and the axes of rotation 20, on each of which a gear wheel 21 is arranged. In the embodiment according to FIG. 8, in accordance with the embodiment according to FIG. 1, an external gear ring 36 is formed on the axle bevel gear, which meshes with the gear 35 on the axis of rotation 20. The transmission ratio is therefore smaller than that in the embodiment according to FIG. 5.

A further embodiment of the self-locking differential according to FIG. 9 differs from the embodiments according to FIGS. 5 and 8 in that there is no gear ratio between the axis bevel gears 2 and 4 and the axes of rotation 20 of the gear wheels 21. Therefore, in this embodiment this is coaxial the Achswel¬ le 1 or 3 arranged gear 22 rotatably arranged on the respective axle shaft. Each of these gears 22 is in engagement with four gears 21. Each of these gears 21 works with the gear 22 arranged coaxially on the axle shaft 1 or 3 as a pump or motor. When the oil flow is interrupted by the shut-off devices 26, 27 in the connecting channels 40, the torque is transmitted from the differential basket to the axle shaft via this gear 22. In contrast to this, in the embodiments according to FIGS. 1, 5 and 8, the gear wheel 22 rotatably arranged on the axle shaft 3 is necessary in order to form a pump as a displacement body together with the other gear wheels 21, this gear wheel because of the existing gear ratio, it rotates faster than the axle shaft. 9 is because of the missing 1 5

Gear ratio in the axial direction shorter than the previously described embodiments, but in the remaining parts, these embodiments are completely the same.

5 A further embodiment according to FIG. 10 essentially corresponds to the embodiment according to FIG. 9 and additionally only has an axial piston pump 45 arranged coaxially to the axle shaft 3, which is in the larger chamber in this embodiment

10 33 works, which with the stripper 34; Oil is kept filled. This axial piston pump 45 ^ rotates with the differenti al basket 7a and stands above the valve 31, 32 already described at the beginning, arranged in the differenti al basket, which is preferably a ball -back valve 15, with the working space 23 for the hydraulic

Pump / motor system in connection to ensure that sufficient pressure is always maintained in this work area. This applies to the case that the previously described in the embodiments

20 according to FIGS. 1-9 existing valve 30, 31 does not sufficiently fulfill this task.

The further embodiment of the limited slip differential shown in FIG. 11 represents a further variant in which the differenti al basket 7b into two individual ones

25 housing is divided, so that an existing differential can be expanded with additional components to a limited slip differential. The subdivided differenti al basket 7b includes only the axle bevel gears and the differential bevel gears.

30 of the differential housing 46 and a pump / motor housing 47 connecting in the axial direction and coupled to it in a rotationally fixed manner, through which the axle shaft 3 extends. Between this axle shaft 3 and the pump / motor housing 47 as part of the differenti al -

35 basket 7b is the hydraulic pump / motor system 1 6

interposed, which works exactly as the principle described above in connection with the other embodiments. In the embodiment according to FIG. 11, the parts within the housing 47 match the corresponding parts of the embodiment according to FIG. 1. Thus, the embodiment according to FIG. 11 is a variant of the embodiment according to FIG. 1, in which only the differential basket is divided into two housings. The two housings 46 and 47 are connected to one another in a rotationally fixed manner by a coupling sleeve 48. With this construction, an existing differential can easily be expanded to a self-locking differential.

In the further exemplary embodiment shown in FIG. 12, the same principle is used for locking a power distribution differential, which here is designed as a planetary distribution differential and serves to distribute the engine torque to a front and a rear vehicle drive. A shaft 1 leading to the rear drive axle carries a crown gear or outer wheel 50 and a shaft 3 leading to the front drive axle carries a sun gear 51 and the planet gears 52 of the planetary gear 50, 51, 52 mesh with the sun gear 51 and the crown gear 50. Due to the larger diameter of the crown gear 50, a greater torque is transmitted to the shaft 1 than to the shaft 3 with the sun gear 51 arranged at the end. The planet gears 52, which are present in plurality, are rotatably mounted in the differential basket 7. The further structure corresponds to the embodiment according to FIGS. 1-4. Here, a gearwheel 21 is arranged on the axis of rotation 20 of each planet gear 52 in a rotationally fixed manner 1 7

that forms the displacement body of the hydraulic pump / motor system. Four gearwheels 21 arranged in the annular part 16 interact with a gearwheel 22 arranged on the shaft 3 coaxially to the latter. The differenti al basket 7 is driven via a hollow shaft 53 which surrounds the shaft 3 and by a spur gear 54 which is non-rotatably arranged on this hollow shaft. The planet gears 52 rotatably mounted in the differenti al basket 7 take the crown gear 50 and the sun gear 51 with them, so that the shafts 1 and 3 and the differenti al basket 7 rotate at the same number of revolutions. If a speed difference occurs between the shafts 1 and 3, for example because a drive axle slips, the planet gears 52 rotate about their own axis while they roll on one of the gears meshing with them from the crown gear 50 or sun gear 51. When the planet gears 52 rotate about their own axis, the hydraulic motor / pump system begins to operate in the manner described above and causes the locking, with the result that both shafts 1 and 3 rotate.

In hydraulic pumps of the type described here, there are always leakage losses which are factored in here and lead to the effect that the self-locking differential works softly and elastically and that the

Roll compensation during slow cornering is never impaired.

Claims

Patent claims

1.Self-locking differential for motor vehicles, with a rotatably drivable differenti al basket, in this differential gears rotatably mounted on the differenti al axles and with these engaging axle gears arranged on the two axle shafts, characterized by a between at least one of the two axle shafts (1,3 ) and the differenti al basket (7, 7a, 7b) interposed hydraulic pump / motor system (21-28, 40, 41) with displacement bodies (21, 22) working as a pump or motor, through their working spaces (23) a flow circuit for lines (24, 25, 40, 41) forming the hydraulic medium are connected to one another, in which connecting lines throttling or shut-off devices (26, 27, 28) are arranged, which only prevent the occurrence of a relative rotation between the axle shaft (1 , 3) and differential cage (7, 7a, 7b) using the delivery flow of the pump / motor system if a definable limit value is exceeded or a Block, as a result of which the pump / motor system, which is consequently prevented from rotating or blocked, brings about an at least approximately loss-free torque transmission between the differential basket (7, 7a, 7b) and the axle shaft (1,3).

2. Self-locking differential according to claim 1, characterized in _that between each of the two axle shafts (1,3) and the Differenti al basket (7a) a split between the two hydraulic pumps Achswellenseiten / motor system (21,22,23,40 , 41) with displacement bodies (21, 22) working as a pump or as a motor is whose working spaces (23) through a flow circuit for the hydraulic medium and between the displacement bodies (21,22) on one and on the other Achswel lensei te extending and throttle or

Shut-off devices (26-28) containing lines (40, 41) are connected to each other. .

3. limited slip differential according to claim 1 and

2, characterized by the axle shaft (1,3) in

Rotating displacement body (21), which is in rotary connection with the Ac kweTle, and a further displacement body (22) arranged coaxially to the axle shaft (1, 3) cooperate on this and form a hydraulic pump or motor. |

4. Be bstsperrdiffjerenti al according to claim 3, characterized in that purpose; i multiplication of the number of hydraulic pumps or motors a coaxially to the axle shaft (1,3) arranged on this displacement body (22) with a plurality of at a radial distance from the axle shaft ( 1,3) in the differenti al basket (7, 7a, 7b) rotatably mounted and with the axle shaft (1,3) in rotary connection with the displacement bodies (21) which cooperates on a circle concentric to the axle shaft at equal angular distances from each other in the differenti al basket (7, 7a, 7b) are rotatably mounted.

5. limited slip differential according to claim 4, characterized in that the radial spacing from the axle shaft (1,3) arranged displacement body (21) by means of axes of rotation (20) in radial flanges (14,15) of the differential carrier (7, 7a, 7b) rotatable and that the housing containing the working spaces (23) for the displacement body (21) has a corresponding bore (23) for receiving the displacement body (21), 20th

between the radial flanges (14, 15) arranged, annular part (16, 16a) of the differenti al basket (7, 7a, 7b) is formed.

6. limited slip differential according to claim 4, characterized in that the coaxial to the axle shaft (1,3) displacement body (22) is arranged in a rotationally fixed manner on the axle shaft (1,3) and the majority of these are in engagement and arranged on a concentric circle Displacement body (21) drives directly.

7. limited slip differential according to claim 4 and 5, characterized in that the to the axle shaft (1,3) coaxial displacement body (22) is freely rotating on the axle shaft (1,3) and the majority of which are engaged with it and on a concentric Circularly arranged displacement bodies (21) on their respective rotary axes (20) mounted in the radial flanges (14, 15) of the ^" differential cage (7, 7a, 7b), carry a gear wheel (35) inwards from the inner radial flange (15), which has a gear wheel arranged on the axle shaft (1, 3) in a rotationally fixed manner, for example an external or internal gear ring (36, 42) additionally formed on the axle gear (2, 4) which is in engagement with the differential gears (5), a transmission gear forms the purpose of driving all displacement bodies (21) at a higher speed and, as a result, faster closing of the shut-off elements (26-28) arranged in the connecting lines (24, 25, 40, 41).

8. limited slip differential according to claim 1 and 5, characterized in that between one of the two axle shafts (1,3) and the differential cage (7,7b) interposed hydraulic pump / motor system (21-28) in which the bores ( 23) for accommodating the annular part (16) of the differential carrier (7, 7b) which has displacement bodies (21) from a channel leading to the bore (23) next in the circumferential direction (24, 25), each of which consists of an axial (24) and from this to the bores (23) extending radial channel sections (25) as a connecting line for the hydraulic medium, and that in the axial channel section (24) effective shut-off elements (26-28) or throttle elements are arranged in each of the two possible directions of rotation of the displacement body (21).

9. limited slip differential according to claim 2 and 5, characterized in that between each of the two axle shafts (1,3) and the Differenti al basket (7a) interposed pump / motor system (21,22,40,41) one of the one Axial shaft (1) assigned to the annular part (16a) and a further annular part (16a) assigned to the other axle shaft (3) with bores (23) for receiving the displacement bodies (21) and that each of the bores (23) in one ring-shaped part (16a) 'is connected to an associated bore (23) in the other ring-shaped part (16a) via two channels (40, 41) which extend through the differential cage (7a) and which are in the engagement area of the together form a pump or a motor displacement body (21, 22) into the bore (23) and which in the channel section (40) extending from one side to the other of the differential basket (7a) extends in each of the two possible directions of rotation of the have strainer (21) effective shut-off elements (26-28) or throttle elements.

10. Self-locking differential according to one of the preceding claims, characterized in that the shut-off elements in a channel section (24, 40) arranged and held in the open position by spring force (28) are preferably designed as ball valves (26, 27) which are dependent close the channels (24, 25, 40, 41) from the flow rate of the hydraulic medium. 22

11. Limited slip differential according to one of the preceding claims, characterized in that the displacement bodies (21, 22) of the pump / motor system (2T-28, 40, 41) are gear wheels which operate as gear pumps or gear motors.

12. Limited slip differential according to one of the preceding claims, characterized in that the rotatably drivable differenti al basket (7, 7a, 7b) is enclosed by an outer housing (11), which up to approximately the height of the axle shaft (1,3) the hydraulic medium is filled that a wiper is arranged within the outer housing (11) for stripping (34) the hydraulic medium adhering to the outside of the peripheral differential basket (7, 7 a, 7 b), which stretches the hydraulic medium into between the front end of the differential cage (7, 7a, 7b) and the outer housing (11), which is only open at the wiper (34), guides chamber (33).

13. limited slip differential according to claim 12, characterized in that the chamber (33) via a arranged in the differential carrier (7, 7a, 7b) valve (31, 32) with the working space (23) for the hydraulic medium of the pump / motor Is connected to the system and the valve (31, 32) is a self-sucking valve to compensate for leakage losses, which is held in the closing position by spring action.

14. Self-locking differential according to claim

12, characterized in that in the chamber (33) containing the hydraulic medium there is an axial piston pump (45) connected to the differential basket (7,7a) and arranged coaxially to the axle shaft (1,3) Differenti al basket (7,7a) check valve (31,32) arranged behind the pump (45) communicates with the working space (23) for the hydraulic pump / motor system in order to maintain pressure in the working space (23) of the hydraulic pump / motor system. i 15th, limited slip differential according to one of the preceding claims, characterized in that the differential cage (7b) is subdivided into a differential housing (46) which allows only the axle gears (2,4) and the differential gears (5) and one in the axial direction subsequent pump / motor housing (47) which is coupled in a rotationally fixed manner and through which one of the axle shafts (1, 3) extends, between which axle shaft and the pump / motor housing (47) hydraulic pumping / motor System interposed between now. _|

16. Self-locking differential according to claim 1, characterized in that the differential gears are the planet gears (52) of a planetary distributor differential for power distribution of the engine torque to a front and a rear vehicle drive, which are mounted in the differential basket (7) and with one on one first shaft (1) arranged crown wheel (50) and with a sun shaft (51) arranged on a second shaft (3) are engaged, the two shafts (1, 3) leading to a rear and a front vehicle drive axle and that in the Differenti al basket (7) mounted axes of rotation (20) of the planet gears (52) carry the displacement bodies of the hydraulic pump / motor system (21, 22) which are designed as gear wheels (21) and which are coaxial with the one shaft (3) this arranged and designed as a gear (22) displacement body interact and circulate in a ring-shaped part (16) of the differenti al basket (7) containing the work spaces (23) for the displacement bodies (21, 22), in which a plurality of work spaces (23) arranged circumferentially distributed interconnect Channels (24, 25) are formed, in which shut-off elements (26-28) or throttle elements are arranged.