DE4134421A1 - Controlled hydraulic differential for motor vehicle - has preassembled locking device provided as side extension of differential housing - Google Patents

Abstract

The differential has an external housing (1) containing a driven differential housing (4) housing at least one spline wheel (11, 12) engaging two splines (15, 16) fitted to respective shafts (13, 14), a lamella disc packet (20) providing a differential lock between the differential housing (4) and one of the shafts (13, 14). The lamella disc packet (20) of the locking device (17) is contained in a coupling housing (19) with a cylinder (21) coaxial to the rotation axis containing a ring piston (22) acting on the lamella disc packet (20) via a pressure ring (23). The locking device (17) comprises a pre-assembled module and is provided as a side extension of the differential housing (4). USE - Motor vehicle electronic anti-locking braking regulation.

Description

The invention relates to an external signal controlled, pressure medium operated locking differential of a motor vehicle with features according the preamble of claim 1.

A differential differential with such features is known from EP 03 76 474 A1 knows. In this known solution, the locking of the differential is achieved by axially displacing a shaft that is fixed against rotation on a shaft leading to a drive wheel seated bevel gear, the friction force one between the back side of this bevel gear and a counter surface of the differential case ordered disk pack is increased. This arrangement alone has the disadvantage that with increasing wear of the individual slats there is an ever increasing play between the cone that is acting on them wheel and the differential bevel gear meshing with it. That is, he the interlocking play increases with the consequence that the interlocking of the two bevel gears meshing with each other strong dynamic Alternating stresses are exposed, causing rapid wear and tear and at worst can lead to tooth breakage. Besides, this one known solution of the power transmission mechanism between that in the Ringzy to move lighter-acting ring piston and the differential lock the bevel gear is extremely complex, because it consists of several to store exactly the transmission plungers, connected to them and within the difference tialgehäuses to be attached in a special way and a special Power transmission plate. This motion transmission mechanism is not only relatively complex and therefore expensive, moreover, it was also relative unfriendly, because in the case of defects practically the whole differential that must be taken.

It is therefore an object of the invention to provide a lockable differential differential gangs mentioned type so that its necessary for blocking Components less complicated and expensive, and easy to assemble and disassemble  are cash and there is also the possibility of conventional compensation differences tiale retrofitted in a simple manner with such a locking device.

This object is achieved by a differential with the im Features specified claim 1 solved.

There were advantages in configurations, possible uses and control principles Zipien are specified in the subclaims.

An advantage of the differential differential according to the invention is that that for the blocking of the necessary organs is no longer the same as in the discu initially State of the art quasi in the center of the differential housing, but outside of it are arranged as a lateral extension on this. There by there is the possibility to build all parts of the locking device completely pre-assemble the set and thus also in the retrofit process in the housing install the differential. Further advantages of the invention The following solution describes several solutions Example, the drawing shows in detail:

Fig. 1 shows a longitudinal section through a differential compensation with a first embodiment of locking device according to the invention,

Fig. 2, the lock apparatus of Fig. 1 a longitudinal section in an enlarged illustration in part,

Fig. 3 shows a detailed view X of Fig. 2,

Fig. 4 tung a second embodiment of the present invention Sperreinrich,

Fig. 5 shows an alternative embodiment of the pressure medium supply to the OF INVENTION to the invention locking means,

Fig. 6 shows a detailed view X of Fig. 5,

Fig. 7 is a block diagram of an embodiment for the control of the inventive differential differential.

In the figures, the same or corresponding components are the same Be train sign attracted.

The differential has an outer housing 1 and a differential housing 4 rotatably mounted therein by means of two bearings 2 , 3 . The latter can be driven via an external toothed ring 5 screwed to it by a meshing rit zel 6 , the end of which is mounted on a ge through a bearing in the outer housing 1 and is arranged in connection with the drive device of the motor vehicle in connection with the drive shaft 8 . Within the differential housing 4 , two differential bevel gears 11 , 12 are rotatably mounted on an associated bearing pin 9 , 10 , both of which are each in engagement with a rotationally fixed on a drive wheel leading to a shaft 13 , 14 on a bevel gear 15 , 16 .

This as previously described conventional embodiment of the differential differential is now assigned a special locking device 17 for the purpose of an external signal-dependent, pressure-medium-operated locking device, which according to the invention with its parts completely outside the differential housing 4 on the front side as a lateral extension on a bearing neck 18 of the latter and closing as well around the te out from the differential housing 4 te, leading to a drive wheel shaft 13 and 14 is arranged.

The locking device 17 consists in its main parts of a clutch housing 19 , a disk set 20 included therein and a ring cylinder 21 with an annular piston 22 acting therein with an upstream pressure ring 23 for pressurized actuation of the disk set 20 for a differential lock. The pressure medium supply to the ring cylinder 21 takes place via line members connected to this and to the outer housing 1 , running inside the outer housing, as well as an external feed line 24 (see FIG. 7), which is connected to a connection element on the outside of the housing. The Ringzylin the 21 is axially fixed in the outer housing 1 and not rotatably arranged. Likewise, the annular piston 22 acting in the ring cylinder 21 cannot be rotated, but can only be moved axially. The ring piston 22 delimits a pressure chamber 55 in the ring cylinder 22 , in which the pressure medium serving for differential locking is effective.

The clutch housing 19 consists of an inner sleeve 25 and an outer sleeve 26 , both of which are in axially fixed association with each other, but normally - ie when the disk set 20 is not pressurized - relative to one another with the non-rotating, but axially movably mounted disk plates 27 , 28 are rotatable. The inner sleeve 25 protrudes on one side from the outer sleeve 26 , is also axially supported and arranged coaxially to the shaft 13 or 14 and connected on the end face via a positive toothing 29 to the differential housing 4 . The lamellae ben 27 , 28 of the disk set 20 extend perpendicular to the axis of rotation 30 and are preferably secured against rotation by means of claw teeth on the inner sleeve 25 and outer sleeve 26 . This composite disk set 20 is supported on the side of the introduction of pressure on the pressure ring 23 and on the opposite side on a lock ring 32 , which is secured against rotation via the same claw teeth as the disk plates 27 and 28 in one of the sleeves 25 and 26, respectively is axially supported on a sleeve internal stop 31 or 33 . In the case of the exemplary embodiment according to FIG. 4, this stop is stationary and is formed by a retaining ring 31 inserted into a groove of one of the two sleeves 25 , 26 . This version is used for such differential differentials, which are installed in passenger cars or small commercial vehicles, for example, and therefore only have to transmit and lock a comparatively low torque, with the result that the lamella disc wear is relatively low. In the embodiment according to FIGS. 1 and 2, on the other hand, which compensating differential is used in vehicles, in particular commercial vehicles such as trucks and buses, and consequently has to transmit and lock a relatively high torque, the disk set 20 is via the lock ring 32 on one axially movable stop 33 is supported, which is part of a built in the clutch housing 19 Nachstellvor direction 34 . This readjustment device 34 corrects a lamella disc use automatically in the sense of a displacement / tracking of the lamella disc package 20 to the opposite pressure ring 23 each time the pressure is released, ie the blocking is lifted. Specifically, this adjustment device 34 consists of a first rotation 35 and axially secured on the inner sleeve 25 arranged bush 35 with an outer, a sawtooth profile having steep thread 36 and a second bush 37 , which with a positive fit in the steep thread 36 , but with no play engaging teeth 38 is provided. The second socket 37 has a radial collar on the end face, which on the one hand forms the stop 33 and on the other hand a support for a compression spring 39 , which at its other end in turn on an axially fixed by a retaining ring 40 on one of the two sleeves 25 , 26 fixed counter plate 41 is supported. By this compression spring 39 , the second socket 37 is constantly in contact with the lock ring 32 and thus keep the disk set 20 ge, wherein when the latter is pressurized by the annular piston 22, there is a frictional engagement between the abutting inclined surfaces of steep thread 36 and toothing 38 , at Pressure relief of the Lamellenschei benpaketes 20, on the other hand, this frictional engagement is canceled again and the second bush 37 is adjusted by the compression spring 39 in the direction of the pressure ring 23 .

At its end opposite the pressure ring 23 , the clutch housing 19 is closed by an end plate 42 which is received between two retaining rings 43 , 44 and is axially fixed in the outer sleeve 26 . In addition, the end plate 42 is axially supported on a locking ring 45 inserted in a groove of the shaft 13 or 14 and is preferably arranged on the shaft 13 in a rotationally secured manner via a claw toothing 46 . In addition, the Endplat te 42 inside a coaxial ring projection 47 , on the circular cylindrical outer surface of which it overlaps the inner sleeve 25 radially centered and on the end face 48 of the inner sleeve 25 is axially supported. In order to ensure a relative rotation between the inner sleeve 25 and outer sleeve 26 , the end plate can furthermore be designed according to two different versions. In a first, visible from FIGS. 1 and 2, the outer sleeve 26 is freely rotatable relative to the end plate 42 , but the end plate 42 itself is non-positively connected to the inner sleeve 25 via its ring projection 47 . In the other Versi on (see Fig. 4), the end plate 42 is connected to the outer sleeve 26 via a claw toothing 49 , which preferably corresponds to that in which the lamellar disks also engage. In this case, the inner sleeve 25 is rotatably mounted on the ring projection 47 and is only supported axially on its end face 48 .

The inner sleeve 25 is also at its outer sleeve 26 projecting Be rich over two bearings 50 , 51 rotatable in which it encompasses ring cylinder 21 ge. For this purpose, the inner sleeve 25 has a collar 52 with an axial projection 53 at the end region in question, which has on the end face the claw teeth 29 for the positive connection with the differential housing 4 and serves as a seat for a double-row angular contact ball bearing 50 , which is held radially on the outside in the ring cylinder 21 . In the axial direction, however, the ring cylinder 21 is supported abge on the back of the collar 52 by an axial needle bearing 51 on the inner sleeve 25 . In addition, the ring cylinder 21 with its coaxial Durchgangsboh tion 54 rotatable with a small clearance on the axially projecting part of the inner sleeve 25 is mounted.

The arranged in the ring cylinder 21 and there delimiting the pressure chamber 55 annular piston 22 acts to lock the differential with the axially supported by an axial needle 26 on it at the front pressure ring 23 on the plate disk pack 20 . In the exemplary embodiments shown, the annular piston 22 is secured against rotation within the annular cylinder 21 by means of interlocking elements, for example pins 58 immersed in blind holes 57 . However, it is also possible at any time to secure the ring piston 22 outside the ring cylinder 21 against rotation by appropriate means.

In the exemplary embodiments according to FIGS . 1 to 4, the pressure medium supplying the organs are at the same time also formed to prevent rotation of the ring cylinder 21 . To this end, the annular cylinder 21 through a pressure-tight to it in closed or integrally formed with it the hanger bracket 59 with internal Druckmittelzuführbohrung 60, into the latter with a cylindrical neck 61 pressure-tight immersing Druckmittelüberleitorgan 62 and with the latter pressure-tightly connected Druckmittelanschluß- and -verteilerorgan 63 that a hole 64 in the outer housing 1 is penetratingly secured to the latter, against rotation. On the organ 63 , the external supply line 24 is connected outside.

As an alternative to this, the ring cylinder 21 (as in the exemplary embodiment according to FIGS . 5 and 6) can also be secured against rotation by means of a securing plate 65 fastened in the outer housing 1 , this being provided on the ring cylinder 21 on the outside by a jumping nose 66 which is provided by a claw 67 of the locking plate 65 is overlapped. In this case, the pressure medium is supplied into the Ringzylin of 21 via an internally of the outer casing 1 moved, between a au ßengehäusefesten connection nipple 68 and a ring fixed to the cylinder Anschlußnip pel 69 (see details FIG. 6) extending pressure conduit 70.

The construction of the locking device described above with reference to the drawing makes it possible that the inner and outer sleeves 25 , 26 together with all installed and attached parts including the pressure ring 23 , the ring cylinder 21 and the annular piston 22 and associated bearings 50 , 51 , 56 and At least parts of the pressure medium supply organs can be preassembled to form a complete structural unit which can be inserted into the outer housing 1 of the compensating differential as a cartridge - possibly also for retrofitting conventional differentials. In this lateral lead-in of the cartridge into the outer housing 1 of the tooth composite 29 between inner sleeve 25 and the differential case 4 ago is first made, then the shaft 13 inserted through the inner sleeve 25 in the differential, and then the cartridge direction to the latter by setting the locking ring 45 in axial fixed. Subsequently, the final assembly of the internal pressure medium line paths is carried out, in the case of the exemplary embodiments according to FIGS. 1 to 4 only the organ 63 having to be passed from outside through the bore 64 and then through the organ 62 and finally being screwed onto the outer housing 1 . In the case of the embodiment shown in FIG. 5 u. 6 is on the ring cylinder 21 already pre-assembled pressure line 70 only to be connected to the connecting nipple 68 . From this it can be seen that this final assembly of the locking device according to the invention can be carried out in a very simple and simple manner.

The compensating diff equipped with the locking device according to the invention rential is particularly suitable for anti-slip control in egg equipped with an electronic anti-lock protection system (ABS) Motor vehicle. The blocking of the compensation differential to prevent slippage rentials is achieved through targeted regulation and control of the pressure medium drove with the help of the slightly modified ABS control system accomplished. Here comes the following procedure for external signal dependent Control of locking of the differential differential for use: Below a driver speed threshold of ≦ 5 km / h becomes a permanent lock tion of the differential differential and effective for this lock Pressure of the pressure medium supplied as a function of the driving or gas pressure dal position set. Above the said speed threshold The differential lock is only locked if one is exceeded predetermined speed difference of the driven wheels.  

From Fig. 7 is shown as an embodiment in the form of a block diagram Vorrich device for performing this method with appropriate connection of the differential according to the invention to an ABS control system already existing in the vehicle. Compressed air is used as the pressure medium. In Fig. 7, double lines generally mean lines carrying compressed air, single-line lines mean electrical lines.

In Fig. 7, 71, 72 denote the non-driven wheels of the vehicle front axle, 73 and 74 the wheels of the driven vehicle rear axle, 75 the drive device consisting of engine and transmission. The compensation differential according to the invention connected to the drive device 75 via the drive shaft 8 is designated here by 76 . The brake cylinders assigned to the brakes of the individual wheels 71 , 72 , 73 , 74 are designated with 77 , 78 , 79 , 80 . With 81 compressed air tanks are designated, which are filled by a compressor, not shown. With 82 the service brake pedal and 83 the associated service brake valve is designated. With 84 the accelerator or accelerator pedal and with 85 an associated electric pedal value transmitter. On the service brake valve 83 are the compressed air tank 81 via pressure lines 86 , 87 , via the pressure lines 88 , 89 , 90 on the latter also the rear axle brake circuit, via a pressure line 91 the control element of a relay valve 92 switched into the pressure line 88 and via pressure lines 93 , 94 , 95 the front axle brake circuit closed. The associated ABS / ASR system comprises an electronic ABS / ASR control device 110 , to which a speed sensor 96 , 97 , 98 , 99 , which detects the speed of the ring in conjunction with a pulse arranged on the respective wheel, is detected via electrical lines per wheel, as well as four pressure control valves 100 , 101 , 102 , 103 each installed in one of the pressure lines 89 , 90 , 94 , 95 and a control unit 104 which controls an injection pump servomotor 105 . The control device 104 is also connected to the pedal encoder 85 . The system described so far corresponds to its structure and function according to a known ABS control system. This is now for the purpose of anti-slip regulation (TCS) with the differential according to the invention supplemented by the following construction parts, namely by a pressure control solenoid valve 106 , the output side with the locking device 17 according to the invention of the differential differential 76 via the pressure line 24 and the feed side via a pressure line 107 is connected to the compressed air supply 81 , further an electrical switch 108 and a control device 109 for the actuation of the latter. The switch 108 has two input terminals and one output terminal. The latter is connected to the pressure control solenoid valve 106 . The first input of the switch 108 is connected to the pedal encoder 85 and the second input is connected to the ABS / ASR control unit 110 . The control unit 109 is in turn connected to at least one, but preferably both, of the speed sensors 96 , 97 of the front axle and consequently receives at least one electrical signal representative of the speed of the vehicle. This signal is compared in the control unit 109 with a value corresponding to the predetermined speed threshold of, for example, 5 km / h. Depending on this comparison, the control unit 109 switches when the signaled actual value is smaller than / equal to the internal comparison value, the changeover switch 108 so that the first switching path is switched through, in which the signal coming from the accelerator pedal actuating pedal value transmitter 85 for the control of the pressure control solenoid valve 106 takes effect. However, if the reported speed actual value signal is greater than the internal reference value, the changeover switch 108 is actuated by the control unit 109 and the second switching path switched through, in which then a from the ABS / ASR control unit 110 due to a detected rotational speed - the difference between the driven Wheels 73 , 74 output signal for the control of the pressure control solenoid valve 106 is effective. This means that whenever the first switching path is switched through, the pressure control solenoid valve 106 is actuated proportionally to the Fahrpe pedal actuation, ie the pressure medium pressure supplied to the locking device 17 of the differential equalization proportional to the accelerator pedal actuation is effective. This thus provided pressure acts in the pressure chamber 55 of the locking device 17 to the annular piston 22 and be acting via the latter and the upstream pressure ring 23 corresponding to sammenpressung the slats 27,28 of the flap disc package 20th This results in a certain frictional force which, depending on the size, brakes or prevents the relative rotation between shaft 13 or 14 and differential housing 4 to a greater or lesser extent. Corresponding control of the locking of the compensating differential 76 also takes place when the changeover switch 108 is switched over to its second switching path, but then as a function of signals that are generated in the ABS / ASR control unit 110 .

From the above it can be seen that it is with the Aus according to the invention differential is also possible at any time, previously in a vehicle existing anti-slip acting in conjunction with an ABS via the brakes regulation (ASR) to be replaced.

Claims (20)

1. Controlled by external signal, pressure fluid-operated lockable differential from a motor vehicle, with a rotatably mounted in an outer casing ( 1 ), driven by a drive pinion, differential housing ( 4 ) in which at least one differential bevel gear ( 11 , 12 ) is stored, which with two in each case rotationally fixed on a leading to a drive wheel leading shaft ( 13 , 14 ) seated bevel gears ( 15 , 16 ), and with a locking device with which for a differential housing ( 4 ) and one of the shafts ( 13 , 14 ) effective differential lock, a disk set ( 20 ) can be acted upon by actuators to increase friction, the force being transmitted by an axially adjustable, non-rotatably arranged ring cylinder ( 21 ), also non-rotatable ring piston ( 22 ), characterized in that that the locking device ( 17 ) with its parts completely outside the D ifferentialgehäuses ( 4 ) on the end face as a lateral extension on a La gerhals ( 18 ) of the latter then and around this side out of the Dif ferentialgehäuse ( 4 ), leading to a drive wheel Wel le ( 13 or 14 ) is arranged. 2. Differential differential according to claim 1, characterized in that the disk set ( 20 ) of the locking device ( 17 ) in a clutch housing ( 19 ) is received, namely between an inner sleeve ( 25 ) and an outer sleeve ( 26 ), both in axial are fixed assignment to each other, but usually relative to each other with the ver on them secured against rotation, but axially movably mounted lamellar discs ( 27 , 28 ) that the inner sleeve ( 25 ) also projects axially beyond the outer sleeve ( 26 ), further axially supported and coaxial to the shaft ( 13 or 14 ) and is connected on the end face to the differential housing ( 4 ) in a rotationally fixed manner by means of positive toothing ( 29 ). 3. Differential differential according to claim 2, characterized in that the inner sleeve ( 25 ) is also rotatably supported via bearings ( 50 , 51 ) in which it encompasses ring cylinder ( 21 ), and that in the ring cylinder ( 21 ) to orderly and there a pressure chamber ( 55 ) limiting annular piston ( 22 ) with a via an axial needle bearing ( 56 ) supported on it at the front pressure ring ( 23 ) for differential locking on the disk set ( 20 ) acts. 4. Differential differential according to claims 2 and 3, characterized in that in the clutch housing ( 19 ) is an adjusting device ( 34 ) is built, the automatic disc wear in the sense of lifting a differential lock after corresponding pressure relief of the annular piston ( 22 ) corrected a displacement / tracking of the disk pack ( 20 ) to the pressure ring ( 23 ). 5. Differential differential according to claim 3, characterized in that the external pressure fluid supply members are also designed to take over the function of the anti-rotation device for the ring cylinder ( 21 ), such that the ring cylinder ( 21 ) via a pressure-tightly connected to it or integrally formed with it Holding block ( 59 ) with an internal pressure medium supply bore ( 60 ), a pressure medium supply element ( 62 ) which plunges into the latter in a pressure-tight manner and a pressure medium connection and distributor element ( 63 ) which is connected to the latter in a pressure-tight manner and is fastened to the outer housing ( 1 ) and is secured against rotation . 6. Compensating differential according to claim 3, characterized in that the ring cylinder ( 21 ) on a secured to the outer housing ( 1 ) securing plate ( 65 ) is secured against rotation, and that the pressure medium supply to the ring cylinder ( 21 ) relocated via an outer housing, between a pressure line ( 70 ) extending from the outer housing and an annular cylinder-fixed connection nipple ( 68 , 69 ). 7. Differential differential according to claim 2, characterized in that the clutch housing ( 19 ) on its side opposite the pressure ring ( 23 ) is closed by an end plate ( 42 ) which is axially arranged by two inner and outer locking rings ( 43 , 44 ) the outer sleeve se ( 26 ) fixed, also axially countered from the outside on the shaft ( 13 and 14 ) supported and connected to the latter via a claw toothing ( 46 ) secured against rotation, and that the end plate ( 42 ) also with an inner coaxial Ring projection ( 47 ) the inner sleeve ( 25 ) radially zen trated and countered axially in the pressure direction, but generally thus the outer sleeve ( 26 ) and inner sleeve ( 25 ) is coupled that a relative rotation of the same is possible. 8. Differential differential according to claim 7, characterized in that the end plate ( 42 ) between the retaining rings ( 43 , 44 ) in the same manner as the disk discs ( 28 ) is also secured against rotation in the outer sleeve ( 26 ), and that the inner sleeve ( 25 ) with a Re relative rotation allowing radial play on the ring projection ( 47 ) of the end plate ( 42 ) is mounted. 9. Differential differential according to claim 7, characterized in that the inner sleeve ( 25 ) sits radially non-positively on the annular projection ( 47 ) of the end plate ( 42 ) and the outer sleeve ( 26 ) relative to the end plate ( 42 ) is freely rotatable. 10. Differential differential according to claim 7, characterized in that the inner sleeve ( 25 ) at its end plate ( 42 ) opposite end egg nen to the radially outwardly extending collar ( 52 ) with front axial projection ( 53 ), which in turn has the claw teeth on the front tion ( 29 ) for the positive connection with the differential housing ( 4 ) and also serves as a seat for a double-row angular ball ger ( 50 ), which is gripped radially on the outside in the ring cylinder ( 21 ), which in turn in the axial direction on the back the federal ( 52 ) by an Axialna dellager ( 52 ) on the inner sleeve ( 25 ) and with its through bore ( 54 ) rotatably arranged with play on the latter. 11. Differential differential according to claim 2, characterized in that the disk set ( 20 ) within the two sleeves ( 25 , 26 ) on the side opposite the pressure ring ( 23 ) on a lock ring ( 32 ) which is in the same way as the disk disks ( 27 or 28 ) is secured against rotation in one of the sleeves and supported on a stop. 12. Differential differential according to claim 11, characterized in that the stop is arranged in a stationary manner and is formed by a securing ring ( 31 ) inserted into a groove of the inner sleeve ( 25 ). 13. Differential differential according to claims 4 and 11, characterized in that the stop is movable and formed by part of the clutch inner adjustment device ( 34 ). 14. Differential differential according to claim 13, characterized in that the adjusting device ( 34 ) from a first, rotationally and axially secured on the inner sleeve ( 25 ) arranged socket ( 35 ) with an outer, a sawtooth profile having steep thread ( 36 ) and a second book se ( 37 ), which is provided with a positive fit in the steep thread ( 36 ) but with no play engaging teeth ( 38 ) that the second bushing ( 37 ) the movable stop on which the Lamellenscheibenpa ket ( 20 ) over the counter ring (32) is supported, forms, and is held by a compression spring (39) constantly in abutment contact with the lock ring (32), wherein upon pressurization of the flap disc package (20) from the annular piston (21) produces a frictional engagement between the abutting rest against the sloping flanks of steep thread ( 36 ) and associated toothing ( 38 ) is given, with pressure relief of the disk pack ( 20 ) against this re The connection is canceled again and the second bushing ( 37 ) is readjusted by the compression spring ( 39 ). 15. Differential differential according to claim 3, characterized in that the annular piston ( 22 ) within the ring cylinder ( 21 ) is secured against rotation by positive interlocking members ( 57, 58 ). 16. Differential differential according to one or more of the preceding claims, characterized in that the inner and outer sleeves ( 25 , 26 ) together with all installed and attached parts and together with the pressure ring ( 23 ), the ring cylinder ( 21 ), the The annular piston ( 22 ) and associated bearings ( 50 , 51 , 56 ) and at least parts of the pressure medium supply members form a completely preassembled structural unit which can be inserted into the outer housing ( 1 ) as a cartridge - if necessary also for retrofitting conventional differentials. 17. Differential differential according to the preceding claims, characterized net due to its use for anti-slip control in one with a  electronic anti-lock braking system (ABS) equipped force vehicle. 18. Differential differential according to claim 17, characterized in that the Locking to prevent slippage through targeted regulation and control of the pressure medium supply with the help of the minor modified ABS control system is accomplished. 19. A method for external signal-dependent control of the locking of the differential differential according to claims 1 to 16 when used according to claims 17 and 18, characterized in that below a driving speed threshold of ≦ 5 km / h causes a permanent locking of the differential differential ( 76 ) and the pressure of the pressure medium effective for this locking is set as a function of the driving or accelerator pedal position; on the other hand, above said speed, the locking of the differential differential ( 76 ) thresholds only when a predetermined speed difference of the driven wheels ( 73 , 74 ) is exceeded. is effected. 20. Device for performing the method according to claim 19, characterized in that a pressure control solenoid valve ( 106 ) is provided that on the one hand with a pressure medium source ( 81 ) which also supplies the braking system of the vehicle, and on the other hand with the pressure medium connection ( 24 ) the locking device ( 17 ) of the differential ( 76 ) is connected, that the pressure control solenoid valve ( 106 ) is connected on the control side to an electrical switch ( 108 ) which can assume two switch positions and is actuated by a control unit ( 109 ), which at least receives an electrical signal representative of the driving speed, compares it with a value corresponding to the specified speed threshold of ≦ 5 km / h and, if the actual value signal is less than or equal to this value, switches through the first switching path in which the one Pedal value sensor ( 85 ) coming in e signal for the control of the Drucksteuer-Magnetven valve ( 106 ) is effective, but then when the actual value signal is greater than the comparison value, the second switching path switches through, in which a speed determined by the ABS / ASR control unit ( 110 ) Difference between the driven wheels ( 73 , 74 ) output signal for controlling the pressure control solenoid valve ( 106 ) is effective.