DIFFERENTIAL ARRANGEMENT

Description

[0001] The present application relates to a differential arrangement, in particular for a drive axle of a motor vehicle. The differential arrangement comprises a drive wheel, a differential gear with an input part, and a shift clutch effectively arranged between the drive wheel and the differential gear, wherein, in the closed state of the shift clutch, torque is transmitted from the drive wheel to the differential gear, and in the open state of the shift clutch, torque transmission is interrupted. A first clutch part of the shift clutch is rigidly connected to the input part or to a differential housing of the differential gear, and a second clutch part of the shift clutch is rigidly connected to the other part of the input part and the differential housing, respectively.

[0002] A differential arrangement is known from DE 10 2009 056 088 A1. The differential arrangement comprises a drive wheel; a differential gear with one input part and two output parts, wherein the output parts are drive-connected to the input part and have a compensating effect on each other. A clutch is effectively arranged between the drive wheel and the differential gear, wherein, in the closed state of the clutch, torque is transmitted from the drive wheel to the differential gear, and in the open state of the clutch, torque transmission is interrupted. A controllable actuator is provided for actuating the clutch, and a sensor is provided for determining at least three switching positions of the clutch.

[0003] From DE 10 2013 111 891 A1, a drive arrangement, particularly for use in the drivetrain of a motor vehicle, is known. The drive arrangement comprises a rotatably driven housing, an output part, and a clutch arranged between the rotatably driven housing and the output part. The clutch has a first clutch part that is fixed relative to the housing and axially movable, and a second clutch part that is rigidly connected to the output part and arranged in the rotatably driven housing. A controllable actuator is provided for actuating the clutch. A encoder element is axially movable when the clutch is actuated, and a sensor detects the clutch's switching positions. The first clutch part has an annular section arranged outside the housing and several cam elements that extend axially from the annular section through openings in the housing into the interior of the housing.

[0004] DE 197 16 386 A1 relates to a compensating device or differential device for a vehicle with selectable four-wheel drive, wherein the drive power can be interrupted when switching from four-wheel drive to two-wheel drive. Furthermore, the compensating device has a mechanism for reducing the friction losses of the device when it is not driven. The compensating device is rotatably mounted in a compensating carrier, on the sides of which output shafts are arranged. The drive power of the engine is interrupted when switching from four-wheel drive to two-wheel drive, and the drive power of the engine can be distributed to the left and right output shafts of the vehicle in the four-wheel drive state. An outer compensating housing is rotatable by means of the drive power of the engine.An inner compensating housing is rotatably mounted coaxially within the outer compensating housing, the inner compensating housing being essentially cylindrical. A coupling element is mounted in the outer compensating housing adjacent to the inner compensating housing and movably in the axial direction of the outer compensating housing, the coupling element being essentially cylindrical and rotatably connected to the outer compensating housing together. A pair of claws are mounted in the outer compensating housing so as to engage with each other and be separable from each other, one claw being arranged on an axial end face of the inner compensating housing facing the coupling element, and the other claw being arranged on an axial end face of the coupling element facing the inner compensating housing.A differential gear system is arranged in the inner differential housing, the differential gear system being designed as a bevel gear transmission. Actuating means are provided for actuating the clutch component such that the jaws can be engaged or disengaged from one another in connection with the shifting process between the four-wheel drive and the two-wheel drive of the vehicle, the actuating means being mounted on the differential carrier adjacent to the clutch component. A plurality of holes may be provided in an outer wall section of the outer differential housing, arranged circumferentially, the clutch component being provided with a plurality of legs that can be engaged with the respective holes such that the clutch component is rotatably connected to the outer differential housing.The holes and legs each have opposing side surfaces which are conically converging outwards in the axial direction of the compensating device, whereby cams are present on the opposing side surfaces of the respective holes and legs and the claws can be pre-tensioned to engage with each other when the outer compensating housing is rotated.

[0005] US Patent 2018 / 099562 A1 discloses a differential device comprising a differential housing and a first engagement element with engagement teeth on a first side wall of the differential housing. A coupling element is arranged axially between the first side wall and a second side wall of the differential housing. The coupling element has a second engagement element. A compression element is arranged between the second side wall and the coupling element such that the compression element is compressed axially. When an actuator does not generate a compression force, the first engagement element and the second engagement element are engaged by the compression force of the compression element, and the differential housing and the input element are connected via the coupling element. The first engagement element is disengaged by the second engagement element through a compression force when the actuator is actuated.

[0006] US 10,012,300 B2 discloses a coupled component comprising a first element, a second element, and a coupling. The first element may have an output section. The second element may have an input section located within the output section. The coupling may include multiple first locking elements and a control element for coordinating a radially inward movement of the first locking elements to actuate the coupling of the output and input sections.

[0007] An axially movable coupling element, which is either arranged inside the differential housing and actuated via elements extending axially through openings from the interior of the differential housing, or which is at least partially arranged outside the differential housing and is connected to another coupling element in a torque-transmitting manner via elements extending axially through openings into the interior of the differential housing, is subject to high mechanical stress and is therefore complex in design and expensive in production.

[0008] One task might be to provide a differential arrangement in which the coupling parts can be designed more simply.

[0009] The problem is solved by each of the subject matter of independent claims 1, 6 and 9.

[0010] All three solutions consist of a differential arrangement, in particular for a drive axle of a motor vehicle, comprising a drive wheel, a differential gear with an input part and a shift clutch effectively arranged between the drive wheel and the differential gear, wherein in the closed state of the shift clutch torque is transmitted from the drive wheel to the differential gear and in the open state of the shift clutch torque transmission is interrupted, wherein a first clutch part of the shift clutch is rigidly connected to a differential housing of the differential gear and a second clutch part of the shift clutch is rigidly connected to the input part.The shift clutch has coupling elements that are displaceable relative to the first clutch part and the second clutch part, and at least one switching element acting on the coupling elements, wherein the switching element displaces the coupling elements between a first position for the closed state of the shift clutch, in which the coupling elements are arranged to transmit torque between the first clutch part and the second clutch part, and a second position for the open state of the shift clutch, in which the first clutch part is separated from the second clutch part, wherein at least six coupling elements are provided.

[0011] The input component of the differential gear refers, for example, to a differential carrier, also known as a differential cage. Output components of the differential assembly can be side gears when using a bevel gear or crown gear differential, or a ring gear or sun gear when using a planetary gear differential. The clutch is designed, in particular, as a positive-locking clutch.

[0012] One advantage of the differential arrangement is that the torque-transmitting connection can be established and disconnected without moving either coupling part, thanks to the coupling elements that are movable relative to the first and second coupling parts. This simplifies the design of at least one of the coupling parts. In particular, no coupling part needs to be actuated by an actuator. The fact that the shift clutch has at least six coupling elements has the advantage of distributing the torque transmission across them, allowing each individual coupling element to be manufactured with less stringent strength requirements. For example, the coupling elements can be evenly distributed around the circumference of the shift clutch. The torque load is then advantageously distributed evenly across all coupling elements.Using a larger number of small coupling elements allows for a saving of installation space required for the clutch. Higher torques can be advantageously transmitted via a larger number of coupling elements. This makes the clutch advantageously scalable. In particular, at least 8 coupling elements can be provided. Up to 20 coupling elements are conceivable, and even more with correspondingly larger differential arrangements.

[0013] The torque is transmitted directly from the first coupling part to the coupling elements, or vice versa. Likewise, the torque is transmitted directly from the second coupling part to the coupling elements, or vice versa. According to the invention, the coupling elements are guided in openings of the first coupling part or the second coupling part. In the closed state of the clutch, the switching element in the first position allows the coupling elements to protrude from the openings, so that the coupling elements engage in recesses of the respective other parts of the first and second clutch parts. In the open state of the clutch, the switching element in the second position allows the coupling elements to retract from the recesses into the openings.The coupling elements protrude from the openings by extending beyond an outer contour of the respective coupling part in at least one direction, without being positioned completely outside the coupling part. A coupling element is considered to have retracted into the openings if it no longer extends beyond the contour of the coupling part in the same direction.

[0014] The switching element is, for example, held coaxially to the first coupling part and axially displaceable between the first and second positions. A controllable actuator can be provided to actuate the switching clutch, the actuator advantageously acting on the switching element and moving it from the second position to the first position. The actuator can optionally also move the switching element from the first position to the second position, with the switching element alternatively being pre-tensioned towards the second position by means of a spring. Advantageously, the actuator acts on the switching element, which does not participate in the torque transmission between the coupling parts. Thus, the switching element, as a movable part, can be designed simply, since it is subject to comparatively low mechanical stress. In all embodiments, axial, coaxial, and radial refer to spatial directions.Alignment of components refers to an axis of rotation of the differential gear around which, for example, the drive wheel, the input part and the side shaft gears rotate, unless another axis is expressly specified as the reference.

[0015] According to one embodiment, the coupling elements are designed as balls or cylindrical pins. The diameter of the balls or cylindrical pins can be between five and fifteen millimeters, particularly between eight and twelve millimeters. The torque is transmitted directly from the first coupling element to the spherical or cylindrical surface of the coupling elements, or vice versa. Likewise, the torque is transmitted directly from the second coupling element to the spherical or cylindrical surface of the coupling elements, or vice versa. A cylindrical pin is understood to be a pin of essentially cylindrical shape, which may optionally have grooves or similar recesses in the longitudinal or circumferential direction.

[0016] According to the first and second solutions, the coupling elements are guided axially displaceably in axial openings of the first coupling part. These axial openings of the first coupling part are designed, for example, as axially through bores in the differential housing. The switching element can thus have a ring section acting on the coupling elements from outside the differential housing.

[0017] According to the first solution, the coupling elements are designed as cylindrical pins and are guided axially displaceably in the axial openings of the first coupling part. The cylindrical pins as coupling elements can be rigidly connected to the switching element. For example, the coupling elements are positively connected to the switching element in the axial direction. Advantageously, the switching element can serve as a sensor element for determining the switching positions of the clutch.

[0018] The cylindrical pins, acting as coupling elements, can have conical head sections at their end facing the second coupling part, with the head sections tapering axially from the second coupling part towards the first coupling part. Furthermore, the recesses of the second coupling part can widen axially from a surface facing the first coupling part into the second coupling part. The conical head sections and / or the widening recesses are advantageously suited to retain the coupling elements in the recesses by means of sufficient frictional forces between the conical head sections and the walls of the recesses, thus preventing unintentional disengagement of the clutch, particularly when little or no torque is transmitted via the coupling elements between the first and second coupling parts.

[0019] According to the first solution, the recesses of the second coupling part are designed as elongated holes, the greatest extent of which is arranged circumferentially, thus facilitating the adjustment of the cylindrical coupling links into the first position. The number of recesses in the second coupling part can be greater than the number of coupling links, for example, by an integer multiple of the number of coupling links.

[0020] According to the second solution, at least one switching element has pins that engage in the axial openings, with the coupling elements being designed as balls. When the switching coupling is closed, the coupling elements are held by the pins in the recesses of the second coupling part. Guide sleeves can be arranged in the axial openings to guide the coupling elements.

[0021] According to the third solution, the coupling elements are guided radially displaceable within radial openings of the second coupling part. At least one switching element has a switching contour that acts on the coupling elements to displace them. In the second position, the switching contour retracts the coupling elements into the radial openings of the second coupling part, and in the first position, it partially pushes them out of the radial openings.

[0022] The radial openings of the second coupling part can be designed as radially through bores in the input part. When the clutch is closed, the coupling elements are locked radially by the at least one switching element. This is particularly advantageous when the switching element is arranged radially between the second coupling part and the differential housing. The at least one switching element can have a sleeve-shaped section with the switching contour. Alternatively, the switching element can also have ring-shaped pins, with each pin acting on one coupling element.

[0023] The at least one switching element has, for example, at least one projection extending axially through an opening in the differential housing, wherein the switching element can be actuated by the actuator via the at least one projection. The at least one projection can further be connected, for example, to a sensor element for determining the switching positions of the clutch.

[0024] Examples of implementation are explained below with reference to the drawing figures. These show: Fig. 1 a differential arrangement with a shift clutch according to the third solution in longitudinal section in the open shift position of the shift clutch; Fig. 2 the differential arrangement according to Fig. 1 in the closed switching position of the clutch; Fig. 3 the differential arrangement according to Fig. 2 in perspective view; Fig. 4 the differential arrangement according to Fig. 2 in cross-section; Fig. 5 a differential arrangement with a shift clutch according to the second solution in longitudinal section in the open shift position of the shift clutch; Fig. 6 the differential arrangement according to Fig. 5 in perspective view; Fig. 7 a detail of the differential arrangement according to Fig. 5 in longitudinal section; Fig. 8 the differential arrangement according to Fig. 5 in the closed switching position of the clutch; Fig. 9 the detail according to Figure 7 in the closed switching position of the clutch; Fig. 10 a differential arrangement with a shift clutch according to the first solution in longitudinal section in the open shifting position of the shift clutch; Fig. 11 the differential arrangement according to Fig. 10 in perspective view; Fig. 12 a detail of the differential arrangement according to Fig. 10 in longitudinal section; Fig. 13 the differential arrangement according to Fig. 10 in the closed switching position of the clutch; Fig. 14the differential arrangement according to Fig. 13 in perspective view; Fig. 15 the detail according to Figure 12 enlarged view; Fig. 16 the differential arrangement according to Fig. 10 in cross-section; Fig. 17 the detail according to Figure 15 according to an alternative embodiment; Fig. 18 a detail of the differential arrangement according to Fig. 10 in perspective view; Fig. 19 the detail according to Fig. 18 in another perspective view; Fig. 20 the detail according to Fig. 18 in another perspective view; Fig. 21 A drive arrangement with the differential arrangement in schematic representation.

[0025] The Figures 1 to 4 show a differential arrangement 2 according to the invention for a drive axle in a drive arrangement of a motor vehicle according to Figure 20 in a first embodiment and are described together below. Figure 1Figure 2 shows the differential arrangement 2 with a shift clutch 4 in the open shift position of the shift clutch 4 in a longitudinal section. Figure 2 shows the longitudinal section of the differential arrangement in the closed switching position of the shift clutch 4. Figure 3 shows the differential arrangement in perspective view and Figure 4 a cross-section along line BB in Figure 1A differential arrangement 2 is shown, comprising a differential gear 3, a clutch 4, and an actuator 5 for actuating the clutch 4. A drive wheel 6, rigidly connected to a differential housing 7, is provided for transmitting torque from a drive motor (not shown). The differential housing 7 is constructed in two parts, comprising a first cup-shaped housing part 8 and a second cup-shaped housing part 9, the second housing part 9 being integrally formed with the drive wheel 6. The first housing part 8 is rigidly connected to the second housing part 9, in particular by welding. It is understood that the connection between the drive wheel 6 and the differential housing 7, or between the first housing part 8 and the second housing part 9, can also be made in other ways, for example, by bolted connections or other conventional fasteners.The differential gear 3 is arranged in the differential housing 7 and can be driven to rotate about a rotary axis A.

[0026] The differential gear 3 comprises a differential carrier 13, which has a substantially cylindrical outer surface 14. The differential carrier 13 is mounted to a corresponding inner cylindrical surface section 15 of the first housing part 8 so as to be rotatably slid about the axis of rotation A. Two bores are provided in the differential carrier 13, into which a pin 17 is inserted. Two differential gears 19 are rotatably mounted on the pin 17 about a pin axis B. The two differential gears 19 mesh with a first and a second side shaft gear 20, 22, which are arranged coaxially with the axis of rotation A. The two side shaft gears 20, 22 each have longitudinal teeth 23, into which a corresponding mating tooth of a side shaft engages. Figure 20) for torque transmission. The first side shaft gear 20 is axially supported relative to the first housing part 8, with a sliding disc preferably arranged between the first side shaft gear 20 and the support surface of the first housing part 8. Similarly, a sliding disc is also arranged between the second side shaft gear 22 and the second housing part 9 to support the axial forces.

[0027] The shift clutch 4 is designed as a positive-locking clutch. The positive-locking shift clutch 4 comprises a first clutch part 25, which is rigidly connected to the differential housing 7, and a second clutch part 26, which is rigidly connected to the input part 13, as well as ten coupling elements 10, which are displaceable relative to the first clutch part 25 and the second clutch part 26, and a switching element 12 acting on the ten coupling elements 10. In the closed state of the shift clutch 4, a torque is transmitted between the first clutch part 25 and the second clutch part 26 via the coupling elements 10, while in the open state of the shift clutch 4, the coupling elements 10 do not transmit any torque. Figure 1The clutch 4 is shown in the closed state. The switching element 12 is in a first position, in which it holds the coupling members 10 in a torque-transmitting manner between the first clutch part 25 and the second clutch part 26. In the Figure 2The clutch 4 is shown in the open position. The switching element 12 is in a second position, in which it releases the coupling links 10, so that the first clutch part 25 is separated from the second clutch part 26 and the torque transmission is interrupted. The coupling links 10 are guided in openings 11, either in the first clutch part 25 or the second clutch part 26. When the clutch 4 is closed, the switching element 12, in its second position, allows the coupling links 10 to protrude from the openings 11, so that the coupling links 10 engage in recesses 21 of the respective first clutch part 25 and the second clutch part 26. When the clutch 4 is open, the switching element 12, in its second position, allows the coupling links to retract from the recesses 21 into the openings 11.The switching element 12 is held coaxially to the first coupling part 25 and is axially displaceable between the first position and the second position. A controllable actuator 5 is provided for actuating the switching clutch 4 by moving the switching element 12 from the second position to the first position.

[0028] In the embodiment according to the Figures 1 to 4The ten coupling elements 10 are designed as radially displaceable balls guided in radial openings 11 of the second coupling part 26. The switching element 12 has a switching contour 45 that acts on the coupling elements 10. The switching contour 45 is a receptacle into which the spherical coupling elements 10 can retract. When the switching element 12 is moved axially from the second position to the first position, the switching contour 45 pushes the coupling elements 10 out of the openings 11, which are designed as radially through bores in the input part 13, beyond the outer contour of the second coupling part 26, acting like a wedge. When the switching clutch 4 is closed, the coupling elements 10 are locked radially by the at least one switching element 12, which is arranged radially between the second coupling part 26 and the differential housing 7.

[0029] The switching element 12 has at least one projection 27 extending axially through an opening 28 in the differential housing 7, such that the switching element 12 can be actuated by the actuator 5 via the at least one projection 27. The at least one projection 27 is further equipped with a sensor element 38 for a sensor (44, Figure 20) for determining the switching positions of the switching clutch 4. A return spring 43 is arranged between the differential housing 7 and the encoder element 38. The return spring 43 is designed in this case as a disc spring, although it is understood that other spring types, for example coil springs, can also be used. The switching element 12 can have a sleeve-shaped section with the switching contour 45, wherein the projection(s) 27 extend axially from the sleeve-shaped section. Alternatively, the switching contour 45 can also be arranged on coaxially ring-shaped axial pins, with each pin being assigned to a coupling element 10.

[0030] Sensor 44 ( Figure 20The sensor 44 is arranged axially in the area of ​​the actuator 5 and interacts with the encoder element 38. The sensor 44 can be designed as a Hall sensor, which can detect the distance to the encoder element 38 without contact. However, another non-contact sensor can also be used, for example, an inductive sensor. In the open position of the switching clutch 4, the encoder element 38 is axially close to the sensor 44. This position, in which the switching clutch 4 is open, is described in the Figure 1 shown. In the Figure 2 In contrast, a switching state is shown in which the shift clutch 4 is engaged for torque transmission from the drive wheel 6 to the differential carrier 13. It can be seen that the encoder element 38, together with the shift element 12, is moved relative to the sensor 44 in the direction of the first clutch part 25 or the differential gear 3.

[0031] The Figures 5 to 9show a further embodiment of the differential arrangement 2. This largely corresponds to the embodiment according to the Figures 1 to 4 , so that the above description applies with regard to the commonalities. Identical or modified components are assigned the same reference numbers, as in the Figures 1 to 4 . Figure 5 shows the differential arrangement 2 with the shift clutch 4 in the open shift position of the shift clutch. Figure 6 shows the differential arrangement in a perspective view. Figure 7 shows a detail of the differential arrangement in a longitudinal section along line CC in Figure 5 . The Figure 8 shows the differential arrangement 2 in the closed switching position of the shift clutch 4 and Figure 9 the detail of the differential arrangement in a longitudinal section along line CC in Figure 7 The following refers to the Figures 5 to 9 The differences were discussed.

[0032] The special feature of the present embodiment lies in the fact that the spherical coupling elements 10 are guided axially displaceably in axial openings 11 of the first coupling part 25, wherein the at least one switching element 12 has pins 29 engaging in the axial openings 11, which act on the coupling elements 10. Figure 6 , 8 and 9 The clutch 4 is shown in the closed state. The switching element 12 is in the first position, in which it holds the coupling elements 10, transmitting torque between the first clutch part 25 and the second clutch part 26. Figures 5 and 7The switching clutch 4 is shown in the open state. The switching element 12 is in the second position, in which it releases the coupling elements 10, so that the first clutch part 25 is separated from the second clutch part 26 and the torque transmission is interrupted. In the closed state of the switching clutch 4, the switching element 12, in its first position, allows the coupling elements 10 to protrude from the axial openings 11, so that the coupling elements 10 engage in the recesses 21 of the second clutch part 26. In the open state of the switching clutch 4, the switching element 12, in its second position, allows the coupling elements to retract from the recesses 21 into the openings 11. The switching element 12 is held coaxially with the second clutch part 26 and is axially displaceable between the first and second positions.

[0033] In the closed state of the shift clutch 4, the coupling elements 10 are held by the pins 29 in the recesses 21 of the second clutch part 26. The axial openings 11 of the first clutch part 25 are designed here as axially through bores in the differential housing 7. The shift element 12 has an annular section 30 that acts on the pins 29 from outside the differential housing 7. The actuator 5 acts directly on the annular section 30 to actuate the shift element 12. The encoder element 38 can be arranged on the annular section 30, or the annular section itself can serve as the encoder element 38.

[0034] The Figures 10 to 20 show a further embodiment of the differential arrangement 2. This largely corresponds to the embodiment according to the Figures 5 to 9 , so that the above description applies with regard to the commonalities. Identical or modified components are assigned the same reference numbers, as in the Figures 1 to 9 The differences will be discussed below. Figure 10 shows the differential arrangement 2 with the shift clutch 4 in longitudinal section in the open shift position of the shift clutch 4. Figure 11 shows the differential arrangement in a perspective view. Figure 12 shows a detail of the differential arrangement 2 in a longitudinal section along line CC in Figure 10 In Figure 13 The differential arrangement 2 is shown in the closed switching position of the switching clutch 4. Figure 14 Figure 2 shows the differential arrangement 2 in a perspective view. Figure 15 is the detail from Figure 12 shown in an enlarged view, while Figure 17 The detail is shown in an alternative embodiment. Figure 16 shows the differential arrangement 2 in a cross-section along the line DD in Figure 10 . The Figures 18 to 20The figures show a detail of the differential arrangement 2 in different views. The following refers to the Figures 10 to 20 The differences were discussed.

[0035] In this embodiment, ten coupling elements 10 are provided, which are guided axially displaceably in axial openings 11 of the first coupling part 25. The special feature of the present embodiment is that the coupling elements 10 are designed as cylindrical pins, wherein the coupling elements 10 are rigidly connected to the switching element 12. A cylindrical pin is to be understood as a pin of essentially cylindrical shape, which may optionally have grooves or similar recesses in the longitudinal or circumferential direction.

[0036] In the Figures 13 and 14The switching clutch 4 is shown in the closed state. In the closed state of the switching clutch 4, the switching element 12, in its first position, allows the cylindrical coupling members 10 to protrude from the axial openings 11, so that the coupling members 10 engage in the recesses 21 of the second clutch part 26. Figures 10 to 12 The switching clutch 4 is shown in the open state. In the open state of the switching clutch 4, the switching element 12, in its second position, allows the pin-shaped coupling members 10 to retract from the recesses 21 into the openings 11. The switching element 12 is held coaxially to the second coupling part 26 and is axially displaceable between the first and second positions.

[0037] In the Figure 12 is a section along line CC according to Figure 10The diagram shows in detail the switching element 12 in its second position, i.e., in the disengaged state of the switching clutch 4. One of the coupling elements 10 can be seen having retracted from one of the recesses 21 into one of the openings 11. Figure 15 The detail is shown again enlarged. In the Figure 16 is a section along line DD according to Figure 10The cylindrical coupling member 10 fits into the recess 21, bounded by walls 34. The recess is designed as an elongated slot in the circumferential direction to facilitate adjustment of the coupling member 10 into the second position. The coupling members 10 have a clearance fit with the recess 21 in the second coupling part 26. The clearance is, for example, between 0.02 and 0.06 millimeters in the radial direction. Due to the elongated shape of the recess 21, the clearance in the circumferential direction is 0.6 to 0.8 millimeters greater than in the radial direction. In the illustrated embodiment, the recess 21 is not designed as a complete bore in solid material of the second coupling part 26, but rather on an annular stub of the differential carrier 13, the radial extent of which is smaller than the bore diameter.A clearance between the coupling links 10 and the first coupling part 25 compensates for positional tolerances of the coupling geometry on the differential carrier 13 and for deformations of the differential carrier 13 and the coupling links 10 under load. This clearance can, for example, be between 0.08 and 0.3 millimeters.

[0038] In the Figure 17The detail is shown according to an alternative embodiment. The cylindrical coupling member 10 has a head section 33 facing the second coupling part 26, which engages in the recess 21 when the clutch 4 is closed. This head section 33 has a conical shape, tapering axially from the second coupling part 26 to the first coupling part 25. The recess 21 has a shape approximately opposite to that of the coupling member 10. The recess 21 widens axially from the first coupling part 25 to the second coupling part 26. This shape ensures that the coupling member 10 is held in the recess 21 by friction between the head section 33 of the coupling member 10 and the wall 34 of the recess 21, even under very low applied torques.

[0039] In the Figure 19The switching element 12 or the encoder element 38 is shown without coupling elements. In the Figures 18 and 20 The switching element 12 of the embodiment according to Figure 10The cylindrical coupling elements 10 are shown in perspective detail. They are positively connected to the switching element 12 in the axial direction, for example, by a circumferential groove 31 on the coupling elements 10 being inserted into a corresponding keyhole-shaped opening 32 on the annular switching element 12. A clearance between the coupling elements 10 and the switching element 12 can be, for example, 0.2 millimeters, since there is generally no force transmission between the coupling elements 10 and the switching element 12. Alternatively, the coupling elements 10 can be attached to the annular switching element 12 in a suitable other manner, for example, by a screw connection, by bonding, or by spot welding. In this embodiment, the switching element 12 can serve as a sensor element 29 for the sensor 44 to determine the switching positions of the clutch.Since there is generally no power transmission between the coupling elements 10 and the switching element 12, the switching element 12 can have a low torsional stiffness, which is, for example, less than 20 percent of the torsional stiffness of the first coupling part 25 and the second coupling part 26, in particular less than ten percent.

[0040] The Figure 21Figure 1 shows a schematic representation of a drive arrangement 47 with the differential arrangement 2. The drive arrangement 47 comprises a drive motor 48, which drives the differential arrangement 2, or rather the drive wheel 6 of the differential arrangement 2, via a gear stage 49. The torque introduced by the differential gear 3 when the clutch 4 is engaged is transmitted to the two side shaft gears 20, 22. Corresponding side shafts 50, 52 are inserted into the longitudinal teeth 23 of the side shaft gears 20, 22 in a rotationally fixed manner for torque transmission. At the ends of the side shafts 50, 52 are constant velocity joints 53, 54, which in turn are connected to the wheels 59, 60 of the vehicle via drive shafts 55, 56 and joints 57, 58 for torque transmission. It can be seen that the differential arrangement 2 is rotatably mounted relative to the stationary housing 41 about the axis of rotation A by means of bearings 61, 62. Reference symbol list

[0041] 2 Differential assembly 3 Differential gear 4 Shift clutch 5 Actuator 6 Drive gear 7 Differential housing 8 First housing part 9 Second housing part 10 Coupling links 11 Opening 12 Shifting element 13 Differential carrier 14 Outer surface 15 Surface section 17 Pin 19 Differential gears 20 Side shaft gear 21 Recess 22 Side shaft gear 23 Longitudinal toothing 25 First clutch part 26 Second clutch part 27 Extension 28 Openings 29 Pin 30 Ring section 31 Circumferential groove 32 Keyhole-shaped opening 33 Head area 34 Wall 35 Guide sleeves 38 Sensor element 43 Return spring 44 Sensor 45 Shift contour 47 Drive assembly 48 Motor 49 Gearbox 50 52 Shaft 53, 54 Joint 55, 56 Cardan shaft 59, 60 Wheel 61, 62 Bearing A Pivot B Spindle axle

Claims

1. Differential arrangement, in particular for a drive axle of a motor vehicle, comprising a drive wheel (6); a differential gear (3) with an input part (13); a shift clutch (4) operatively arranged between the drive wheel (6) and the differential gear (3), wherein in a closed state of the shift clutch (4) a torque is transmitted from the drive wheel (6) to the differential gear (3), and in an open state of the shift clutch (4) a torque transmission is disconnected, wherein a first clutch part (25) of the shift clutch (4) is fixedly connected to a differential housing (7) of the differential gear (3) and a second clutch part (26) of the shift clutch (4) is fixedly connected to the input part (13), wherein the shift clutch (4) comprises coupling members (10) displaceably arranged relative to the first clutch part (25) and to the second clutch part (26), and at least one switching element (12) which acts on the coupling members (10), wherein the switching element (12) displaces the coupling members (10) between a first position for the closed state of the shift clutch (4) in which the coupling members (10) are arranged in a torque-transmitting manner between the first clutch part (25) and the second clutch part (26), and a second position for the open state of the shift clutch (4), in which the first clutch part (25) is separated from the second clutch part (26), wherein at least six coupling members (10) are provided, wherein the coupling members (10) are guided in openings (11) of the first clutch part (25) or of the second clutch part (26), wherein, in the closed state of the shift clutch (4), the switching element (12), in the first position, actuates the coupling members (10) to emerge from the openings so that the coupling members engage in recesses (21) of the respective other one of the first clutch part (25) and the second clutch part (26), and wherein, in the open state of the shift clutch (4), the switching element (12), in the second position, actuates the coupling members (10) to recoil from the recesses into the openings (11), wherein the coupling members (10) are guided axially displaceable in axial openings (11) of the first clutch part (25), wherein the coupling members (10) are formed as cylindrical pins, the coupling members (10) being fixedly connected to the switching element (12), wherein the recesses (21) of the second clutch part (26) are formed as elongated holes extending in circumferential direction.

2. Differential arrangement according to one of claims 1 or 2, characterized in that the axial openings (11) of the first clutch part (25) are formed as continuous axial bores of the differential housing (7).

3. Differential arrangement according to one of claims 1 to 3, characterized in that said coupling members (10) comprise a conical head portion (33) facing said second clutch part (26), said head portion (33) tapering in axial direction from said second clutch part (26) towards said first clutch part (25).

4. Differential arrangement according to one of claims 1 to 4, characterized in that the recesses (21) of the second clutch part (26) widen in axial direction from a surface facing the first clutch part (25) into the second clutch part (26).

5. Differential arrangement according to any one of claims 1 to 5, characterized in that the coupling members (10) are positively connected to the switching element (12) in the axial direction.

6. Differential arrangement, in particular for a drive axle of a motor vehicle, comprising a drive wheel (6); a differential gear (3) with an input part (13); a shift clutch (4) operatively arranged between the drive wheel (6) and the differential gear (3), wherein in a closed state of the shift clutch (4) a torque is transmitted from the drive wheel (6) to the differential gear (3), and in an open state of the shift clutch (4) a torque transmission is disconnected, wherein a first clutch part (25) of the shift clutch (4) is fixedly connected to a differential housing (7) of the differential gear (3) and a second clutch part (26) of the shift clutch (4) is fixedly connected to the input part (13), characterized in that the shift clutch (4) comprises coupling members (10) displaceably arranged relative to the first clutch part (25) and to the second clutch part (26), and at least one switching element (12) which acts on the coupling members (10), wherein the switching element (12) displaces the coupling members (10) between a first position for the closed state of the shift clutch (4) in which the coupling members (10) are arranged in a torque-transmitting manner between the first clutch part (25) and the second clutch part (26), and a second position for the open state of the shift clutch (4), in which the first clutch part (25) is separated from the second clutch part (26), wherein at least six coupling members (10) are provided, wherein the coupling members (10) are guided in openings (11) of the first clutch part (25) or of the second clutch part (26), wherein, in the closed state of the shift clutch (4), the switching element (12), in the first position, actuates the coupling members (10) to emerge from the openings so that the coupling members engage in recesses (21) of the respective other one of the first clutch part (25) and the second clutch part (26), and wherein, in the open state of the shift clutch (4), the switching element (12), in the second position, actuates the coupling members (10) to recoil from the recesses into the openings (11), wherein the coupling members (10) are guided axially displaceable in axial openings (11) of the first clutch part (25), wherein the at least one switching element (12) has pins (29) protruding into the axial openings (11), wherein the coupling members (10) formed as balls are held, in the closed state of the shift coupling (4), in the recesses (21) of the second clutch part (26) by the pins (29).

7. Differential arrangement according to claim 7, characterized in that guide sleeves (35) for guiding the coupling members (10) are arranged in the axial openings (11).

8. Differential arrangement according to one of claims 7 or 8, characterized in that the axial openings (11) of the first clutch part (25) are formed as continuous axial bores of the differential housing (7).

9. Differential arrangement, in particular for a drive axle of a motor vehicle, comprising a drive wheel (6); a differential gear (3) with an input part (13); a shift clutch (4) operatively arranged between the drive wheel (6) and the differential gear (3), wherein in a closed state of the shift clutch (4) a torque is transmitted from the drive wheel (6) to the differential gear (3), and in an open state of the shift clutch (4) a torque transmission is disconnected, wherein a first clutch part (25) of the shift clutch (4) is fixedly connected to a differential housing (7) of the differential gear (3) and a second clutch part (26) of the shift clutch (4) is fixedly connected to the input part (13), characterized in that the shift clutch (4) comprises coupling members (10) displaceably arranged relative to the first clutch part (25) and to the second clutch part (26), and at least one switching element (12) which acts on the coupling members (10), wherein the switching element (12) displaces the coupling members (10) between a first position for the closed state of the shift clutch (4) in which the coupling members (10) are arranged in a torque-transmitting manner between the first clutch part (25) and the second clutch part (26), and a second position for the open state of the shift clutch (4), in which the first clutch part (25) is separated from the second clutch part (26), wherein at least six coupling members (10) are provided, wherein the coupling members (10) are guided in openings (11) of the first clutch part (25) or of the second clutch part (26), wherein, in the closed state of the shift clutch (4), the switching element (12), in the first position, actuates the coupling members (10) to emerge from the openings so that the coupling members engage in recesses (21) of the respective other one of the first clutch part (25) and the second clutch part (26), and wherein, in the open state of the shift clutch (4), the switching element (12), in the second position, actuates the coupling members (10) to recoil from the recesses into the openings (11), wherein the coupling members (10) are guided axially displaceable in axial openings (11) of the first clutch part (25), wherein the coupling members (10) are guided radially displaceable in radial openings (11) of the second clutch part (26), the radial openings (11) being formed as continuous radial bores of the input part (13), wherein the at least one switching element (12) has a switching contour (45) acting on the coupling members (10), and wherein, in the closed state of the shift clutch (4), the coupling members are locked in radial direction by the at least one switching element (12).

10. Differential arrangement according to claim 10, characterized in that the at least one switching element (12) has at least one projection (27) extending axially through at least one aperture (28) of the differential housing (7), the switching element (12) being actuated by a actuator (5) via the at least one projection (27), and the at least one projection (27) being connected to an indicator element (38) for a sensor (44) for determining switching positions of the shift clutch (4).

11. Differential arrangement according to one of the preceding claims, characterized in that the coupling members (10) have a diameter between five and fifteen millimeter.

12. Differential arrangement according to any one of claims 1 to 8, characterized in that the switching element (12) serves as an indicator element for a sensor (44) for determining shift positions of the shift clutch (4).