DRIVE ASSEMBLY

Abstract

A drive assembly of a vehicle operable with muscular power and/or motor power. The drive assembly includes: a drive unit; a frame interface, the drive unit being arranged at least partially between a first wall and a second wall of the frame interface, the drive unit including a through-hole; two sleeves inserted into the through-hole of the drive unit on both sides; and a through-bolt inserted through the through-hole and the two sleeves and holding the drive unit on each of the two walls.

Claims

1. A drive assembly of a vehicle operable with muscular power and/or motor power, the drive assembly comprising: a drive unit; a frame interface, the drive unit being arranged at least partially between a first wall and a second wall of the frame interface, and the drive unit includes a through-hole; two sleeves inserted on both sides into the through-hole of the drive unit; and a through-bolt inserted through the through-hole and the two sleeves and holding the drive unit to each of the first and second walls.

2. The drive assembly according to claim 1, wherein the two sleeves contact one another within the through-hole, and the through-bolt clamps the two sleeves against one another.

3. The drive assembly according to claim 1, wherein each of the two sleeve includes a shank and a flange, wherein the shank is arranged at least partially within the through-hole, and the flange is arranged outside the through-hole.

4. The drive assembly according to claim 3, wherein each of the sleeves includes a damping element arranged on a side of the flange that faces the drive unit, and wherein the damping element is formed from a vibration-damping material.

5. The drive assembly according to claim 4, wherein the damping element at least partially surrounds the shank.

6. The drive assembly according to claim 5, wherein at an axial end opposite the flange, the damping element includes a sealing bead axially and radially protruding from the shank.

7. The drive assembly according to claim 6, wherein the sealing bead protrudes in an axial direction from an end face of the shank of the sleeve.

8. The drive assembly according to claim 1, wherein the two sleeves are configured such that in a state fully inserted into the through-hole and in an unclamped state, there is a predefined axial distance between the two sleeves within the through-hole.

9. The drive assembly according to claim 8, wherein the predefined axial distance is such that in the clamped state, the axial distance is compensated by clamping of the two sleeves using the through-bolt and by elastic deformation of the damping element.

10. The drive assembly according to claim 3, wherein: on a side facing a corresponding wall of the frame interface, the flange of at least one of the sleeves includes a plurality of protruding form fit elements, and the form fit elements are configured to press into the corresponding wall as a result of the screw connection to the corresponding wall.

11. The drive assembly according to claim 10, wherein: the flange is formed in two parts and includes a flange base body and an insert ring, the flange base body is formed together with the shank as a one-piece component, and the form fit elements are arranged on the insert ring.

12. The drive assembly according to claim 11, wherein the insert ring is arranged in a groove of the flange base body, and wherein the insert ring is held in the groove by an axial form fit.

13. The drive assembly according to claim 11, wherein the flange base body and the insert ring are formed from different materials, wherein the insert ring has a greater hardness than the flange base body.

14. The drive assembly according to claim 10, wherein each of the form fit elements includes a pyramid or a cone, the pyramid or cone protruding from a surface of the flange.

15. The drive assembly according to claim 14, wherein in the surface of the flange, each of the form fit elements includes a depression adjacent to the pyramid.

16. The drive assembly according to claim 3, wherein: the flange of at least one of the sleeves includes a taper at a radially outer end and on a side facing the shank, and the taper is compensated by the damping element.

17. The drive assembly according to claim 16, wherein the drive unit includes at least one protruding annular rib arranged concentrically with one of the openings, wherein the protruding annular rib and the taper of the flange of the sleeve are arranged on a same radius with respect to a drilling axis of the through-hole.

18. The drive assembly according to claim 1, wherein the through-bolt is fastened to the second wall, and the through-bolt is axially movably held on the first wall.

19. The drive assembly according to claim 18, further comprising: a tolerance compensation element, wherein the first wall includes a first wall opening, wherein the tolerance compensation element is formed in a shape of a sleeve and is arranged within the first wall opening, and a bolt head or a bolt shank of the through-bolt is arranged within the tolerance compensation element.

20. The drive assembly according to claim 19, wherein the tolerance compensation element includes a sliding bearing bushing and a damping shell surrounding the sliding bearing bushing.

21. The drive assembly according to claim 20, wherein the sliding bearing bushing and the bolt head are configured such that the bolt head widens the sliding bearing bushing in a radial direction when the bolt head is arranged within the tolerance compensation element.

22. The drive assembly according to claim 21, wherein the sliding bearing bushing is slotted.

23. The drive assembly according to claim 22, wherein a slot of the sliding bearing bushing is formed obliquely with respect to an axial direction of the sliding bearing bushing.

24. The drive assembly according to claim 20, wherein: the damping shell includes at least one sealing lip on a radially outer side, and the at least one sealing lip is configured such that there is an axial form fit between the damping shell and the first wall when the tolerance compensation element is arranged in the first wall opening.

25. The drive assembly according to claim 24, wherein the damping shell is configured such that the at least one sealing lip is pushed radially outward when the bolt head of the through-bolt is arranged within the tolerance compensation element.

26. The drive assembly according to claim 20, wherein the sliding bearing bushing at at least one axial end includes a radially outward protruding detent lug.

27. The drive assembly according to claim 1, wherein: the through-bolt is fastened to the second wall, the through-bolt clamps the two sleeves and the second wall against one another, the through-bolt is held on the first wall using a retaining element, and the retaining element fixes the through-bolt to the first wall in the radial direction.

28. The drive assembly according to claim 27, wherein: the retaining element is screwed into an internal thread of the wall opening of the first wall using an external thread, and/or the retaining element includes a retaining opening in which a bolt head of the through-bolt is held, and/or the retaining opening widens toward the second wall, and/or the bolt head of the through-bolt is configured to taper toward the first wall.

29. The drive assembly according to claim 27, wherein: the retaining element is arranged in the wall opening of the first wall, and/or the bolt head of the through-bolt includes an external thread, and/or the retaining element is screwed onto the external thread of the bolt head, and/or the retaining element includes a lateral surface tapering toward the second wall, and/or the wall opening of the first wall is configured to taper toward the second wall.

30. The drive assembly according to claim 1, wherein: each of the sleeves includes a press region, and a press fit is formed between the press region and the through-hole.

31. The drive assembly according to claim 1, wherein the through-hole centrally includes a centering region, which has a smaller inner diameter than the rest of the through-hole, for centering the two sleeves.

32. The drive assembly according to claim 1, wherein the through-bolt is a screw, and the through-bolt is screwed into an internal thread of the second wall.

33. The drive assembly according to claim 1, wherein: the through-bolt is a screw, and the through-bolt is screwed into a nut arranged on the second wall.

34. The drive assembly according to claim 33, wherein the nut is arranged in a torsion-proof manner in a recess of the second wall.

35. The drive assembly according to claim 3, wherein: the flange of at least one of the sleeves has a thickness substantially corresponding to a wall thickness of the shank of the sleeve, or the flange of at least one of the sleeves has a thickness corresponding to at least 1.5 times a wall thickness of the shank of the sleeve.

36. A vehicle operable with muscular power and/or motor power, comprising: a drive assembly including: a drive unit, a frame interface, the drive unit being arranged at least partially between a first wall and a second wall of the frame interface, and the drive unit includes a through-hole, two sleeves inserted on both sides into the through-hole of the drive unit, and a through-bolt inserted through the through-hole and the two sleeves and holding the drive unit to each of the first and second walls.

37. The vehicle according to claim 36, further comprising a chainring connected to an output shaft of the drive unit, wherein the second wall of the drive assembly is arranged on a side of the chainring.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0051] The present invention is described below based on exemplary embodiments in connection with the figures. In the figures, functionally identical components are respectively denoted by identical reference signs.

[0052] FIG. 1 shows a simplified schematic view of a vehicle comprising a drive assembly according to a first exemplary embodiment of the present invention.

[0053] FIG. 2A shows a sectional view of the drive assembly of FIG. 1 in the fully screwed state.

[0054] FIG. 2B shows a sectional view of the drive assembly of FIG. 1 before the screwing process.

[0055] FIG. 3 shows a detail of FIG. 2A.

[0056] FIG. 4 shows a perspective detailed view of an assembly of the drive assembly of FIG. 2A.

[0057] FIG. 5 shows a perspective detailed view of a tolerance compensation element of a drive assembly according to a second exemplary embodiment of the present invention.

[0058] FIG. 6 shows a sectional view of a drive assembly according to a third exemplary embodiment of the present invention.

[0059] FIG. 7 shows a sectional view of a drive assembly according to a fourth exemplary embodiment of the present invention.

[0060] FIG. 8 shows a sectional view of a drive assembly according to a fifth exemplary embodiment of the present invention.

[0061] FIG. 9 shows a detail of a drive assembly according to a sixth exemplary embodiment of the present invention.

[0062] FIG. 10 shows a detailed sectional view of FIG. 9.

[0063] FIG. 11 shows a detailed sectional view of a drive assembly according to a seventh exemplary embodiment of the present invention.

[0064] FIG. 12 shows a further detailed sectional view of the drive assembly of FIG. 11.

[0065] FIG. 13 shows a sectional view of a drive assembly according to an eighth exemplary embodiment of the present invention.

[0066] FIG. 14 shows a sectional view of a drive assembly according to a ninth exemplary embodiment of the present invention.

[0067] FIG. 15 shows a sectional view of a drive assembly according to a tenth exemplary embodiment of the present invention.

[0068] FIG. 16 shows a sectional view of a drive assembly according to an eleventh exemplary embodiment of the present invention.

[0069] FIG. 17 shows a detailed sectional view of a drive assembly according to a twelfth exemplary embodiment of the present invention.

[0070] FIG. 18 shows a further detailed sectional view of a drive assembly according to the twelfth exemplary embodiment of the present invention.

[0071] FIG. 19 shows a detailed sectional view of a drive assembly according to a thirteenth exemplary embodiment of the present invention.

DETAILED DESCRIPTION OF EXAMPLE EMBODIMENTS

[0072] FIG. 1 shows a simplified schematic view of a vehicle 100 operable with muscular power and/or motor power and comprising a drive assembly 1 according to a first exemplary embodiment of the present invention. The vehicle 100 is an electric bicycle. The drive assembly 1 is arranged in the region of a bottom bracket and comprises a drive unit 2. The drive unit 2 comprises an electric motor and a transmission and is provided to support the rider's pedal force generated by muscular power, by means of a torque generated by the electric motor. The drive unit 2 is supplied with electrical power by an electrical energy store 109.

[0073] The drive assembly 1 of the first exemplary embodiment is shown in a sectional view in FIG. 2A. The drive assembly 1 comprises a U-shaped frame interface 3 within which the drive unit 2 is partially received. The frame interface 3 is an integral part of a vehicle frame 105 of the vehicle 100 (cf. FIG. 1). The frame interface 3 comprises a first wall 31 and a second wall 32, between which the drive unit 2 is arranged. The first wall 31 and the second wall 32 are connected to one another via a connecting wall 33 and thus formed as a common one-piece component.

[0074] The drive unit 2 is fastened to the frame interface 3 by means of a through-screw connection, as described in more detail below.

[0075] Specifically, the drive unit 2 comprises a through-hole 20 that fully penetrates the drive unit 2 in the transverse direction. In particular, the through-hole 20 is formed in a housing, which is preferably formed from aluminum or magnesium, of the drive unit 2. The housing of the drive unit 2 can be formed in two parts, wherein a housing seal 2c is arranged between the two housing halves 2a, 2b.

[0076] Two sleeves 41, 42 are inserted into the through-hole 20. The two sleeves 41, 42 are inserted into the through-hole 20 starting from a respective side, i.e., at an axial end of the through-hole 20. The sleeves 41, 42 are preferably formed from aluminum or steel.

[0077] Each sleeve 41, 42 comprises a shank 43, which is substantially hollow cylindrical and is inserted into the through-hole 20, and a flange 44. The flange 44 is arranged outside the through-hole and has a larger outer diameter than the shank 43.

[0078] The shank 43 comprises a press region 43a, which is arranged directly adjacent to the flange 44. The press region 43a is designed such that a press fit is formed between the press region 43a and the through-hole 20.

[0079] Formed centrally in the through-hole 20 is a taper region 20a, in which an inner diameter of the through-hole 20 is tapered. Between the taper region 20a and the sleeves 41, 42, a clearance fit is preferably formed. As a result, the taper region 20a brings about a centering of the sleeves 41, 42 and thus a particularly precise arrangement of the sleeves 41, 42.

[0080] Preferably, the two sleeves 41, 42 are identical for a simple and cost-effective production.

[0081] Axial lengths of the sleeves 41, 42, in particular of the shank 43 in each case, are designed in such a way that the sleeves 41, 42 contact one another within the through-hole 20 in the inserted and fully screwed state (as described later).

[0082] Moreover, the drive assembly 1 comprises a through-bolt 5, which is inserted through the through-hole 20 and the two sleeves 41, 42. The through-bolt 5 is designed as a screw and comprises a bolt head 53 at one axial end and an external thread 54 at the other axial end, wherein the external thread 54 extends only over a sub-region of the through-bolt 5.

[0083] By means of the external thread 54, the through-bolt 5 is screwed into a nut 51 on the second wall 32. The bolt head 53 is located on the side of the first wall 31 and in particular abuts against an outer side of the first wall 31.

[0084] Preferably, a clearance fit is respectively formed between the through-bolt 5 and an inner through-opening of the sleeves 41, 42 in order to enable simple insertion. At the regions of the through-bolt 5, within each sleeve 41, 42, a seal, for example an O-ring seal 56, is preferably respectively arranged between the through-bolt 5 and the sleeve 41 or 42 in order to avoid ingress of fluid into the interior of the sleeves 41, 42 and into the interior of the through-hole 20.

[0085] The through-bolt 5 is screwed in such a way that it clamps the two sleeves 41, 42 in the axial direction of the through-bolt 5 against the second wall 32. The sleeves 41, 42 ensure that this clamping does not lead to any or leads to an accurately defined compressive load of the drive unit 2 in the axial direction between the flanges 44 of the two sleeves 41, 42. In particular, a tensile load of the drive unit 2 is avoided as a result of the two sleeves 41, 42.

[0086] The particular through-screw connection of the drive assembly 1 offers numerous advantages. For example, the use of the through-bolt 5 allows for a particularly robust fastening of the drive unit 2. In particular, a screwing process can take place with high torque. By absorbing high compressive forces by means of the sleeves 41, 42, impermissibly high mechanical stress on the drive unit 2 is particularly reliably avoided. Moreover, by adapting the sleeves 41, 42, for example, a tolerance situation of the drive assembly 1 can be simply and cost-effectively adjusted in a defined manner. Furthermore, the through-screw connection allows particularly simple assembly of the drive assembly 1 since the insertion of the through-bolt 5 and actuation of the through-bolt 5 for the screwing-in process can only be carried out from one side, namely from the side of the first wall 31. This is in particular advantageous in the case of limited accessibility on the side of the second wall 32, for example, if there is a chainring 106 on this side (compare FIG. 1).

[0087] Additionally, each sleeve 41, 42 comprises a damping element 45 formed from an elastic and vibration-damping material. In particular, the damping element 45 is formed from an elastomer. Specifically, a radially outer side of the shank 43, of the flange 44, as well as the side of the flange 44 that faces the drive unit 2 are respectively covered or coated with the damping element 45. Preferably, the damping element 45 is thus designed in the form of an overmolding of the sleeve 41, 42.

[0088] Furthermore, the axial lengths of the shanks 43 of the sleeves 41, 42 are designed in such a way that in the state fully inserted into the through-hole 20 and not yet clamped by the through-bolt 5, as shown in FIG. 2B, there is a predefined axial distance 27, i.e., a gap, between the two sleeves 41, 42 in the interior of the through-hole 20. Considered in this case is a state in which the two sleeves 41, 42 are unclamped but the damping element 45 abuts against the drive unit 2 in the region of each flange 44 of each sleeve 41, 42. In particular, the axial lengths of the two shanks 43 are smaller than half of the axial length of the through-hole 20 by a predetermined difference, wherein the predetermined difference is smaller than double the thickness of one of the damping elements 45 in the region of the flange 44.

[0089] In the fully screwed state shown in FIG. 2A, there is a predefined gap 29 between the first wall 31 and the first sleeve 41.

[0090] This particular coordination of the lengths of the two sleeves 41, 42 and of the through-hole 20 achieves that the respective part of the damping element 45 of each sleeve 41, 42 that is located between the flange 44 and the drive unit 2 is partially compressed or clamped between the flange 44 and the drive unit 2 by the clamping by means of the through-bolt 5 and thereby elastically deformed.

[0091] The damping elements 45 and the corresponding design of the sleeves 41, 42 with axial distance in the unclamped state result in a slight compressive load being exerted on the drive unit 2 in the clamped state. This may advantageously affect a tightness of the drive unit 2 itself. Moreover, the elastic deformation of the damping elements 45 enables a particularly reliable seal between the sleeves 41, 42 and the drive unit 2.

[0092] FIG. 1 also shows an output shaft 108, which is rotationally fixedly connected to a chainring 106. The output shaft 108 can in this case be driven by the muscular power of the rider on the one hand and by the motor power of the drive unit 2 on the other hand. The chainring 106 is located on the side of the second wall 32. As already mentioned above, this results in the advantageous accessibility and simplified assembly of the drive assembly 1. Furthermore, this results in the advantage of direct force transmission between the output shaft 108 and the frame interface 3, which can be particularly well absorbed by the direct and robust connection by means of the second wall 32 due to the higher mechanical forces on the chainring side. Moreover, this ensures a defined position of the chainring 106 relative to an axial direction of the output shaft 108 and relative to the frame interface 3, which provides the advantage of a reliably precisely arranged chainline.

[0093] Furthermore, connecting the drive unit 2 and the frame interface 3 via the damping elements 45 results in the advantage of a vibration-decoupled mounting of the drive unit 2 to the vehicle 100. In addition to preventing or reducing a transmission of acoustic vibrations, which has an advantageously effect on noise reduction during operation of the vehicle 100, a transmission of mechanical vibrations is also reduced or prevented. A damaging effect of such vibrations on the screw connection can thus be prevented or reduced. That is to say, loosening or unscrewing the screw connection can be prevented or reduced. Moreover, as a result of the elasticity of the damping element 45 itself, some tolerance compensation can take place, for example with respect to a coaxiality of the bores or openings, or the like.

[0094] Additionally, an axially movable mounting of the through-bolt 5 is provided on the first wall 31. The bolt head 53 of the through-bolt 5 is located within a wall opening 31a of the first wall 31. Deformation of the first wall 31 is thus not provided, but a particularly stiff and robust frame interface 3 can be provided.

[0095] The axially movable mounting is achieved by means of a tolerance compensation element 7. This mounting with the tolerance compensation element 7 is shown enlarged in FIG. 3. The tolerance compensation element 7 comprises a hollow cylindrical sliding bearing bushing 71 and a damping shell 72. The damping shell 72 is in particular formed from an elastic material, preferably an elastomer. The damping shell 72 substantially completely surrounds a radially outer side of the sliding bearing bushing 71, wherein recesses (not shown) can also be provided in the damping shell 72, for example. Additionally, the damping shell at least partially covers both axial end faces of the sliding bearing bushing 71. On the radially inner side, the sliding bearing bushing 71 is exposed so that the bolt head 53 can move smoothly with low friction relative to the tolerance compensation element 7.

[0096] The sliding bearing bushing 71 may preferably be formed from a solid material along the circumferential direction or may alternatively be slotted, i.e., with a longitudinal slot in the axial direction. In both cases, the sliding bearing bushing 71 is preferably designed in such a way that by screwing-in the through-bolt 5 and thus by the bolt head 53 penetrating into the sliding bearing bushing 71, the sliding bearing bushing 71 is widened in the radial direction so that a press fit is produced between the tolerance compensation element 7 and the wall opening 31a. As a result, a mounting of the bolt head 53 in the radial direction without play can be enabled within the wall opening 31a.

[0097] The gap 29 between the first wall 31 and the first sleeve 41 is in this case present both in the unscrewed state and in the fully screwed state (cf. FIGS. 2A and 3).

[0098] Preferably, on a side facing the sleeve 41, the bolt head 53 comprises an insertion chamfer 53a (compare FIG. 3), which facilitates the insertion and screwing-in of the through-bolt 5.

[0099] At the two axial ends, the damping shell 72 comprises a respective sealing lip 72a, which is formed as a lip protruding both radially inward and radially outward. As a result of the elasticity of the damping shell 72, the bolt head 53 pushes the sealing lips 72a radially outward as the through-bolt 5 is screwed in. This results in a reliable and defined seal between the first wall 31 and the tolerance compensation element 7 as well as between the bolt head 53 and the tolerance compensation element 7. Furthermore, the sealing lips 72a bring about an axial form fit of the tolerance compensation element 7 with the first wall 31. This ensures reliable and defined arrangement of the tolerance compensation element 7 relative to the first wall 31.

[0100] As shown in FIG. 4, prior to arranging the drive unit 2, the tolerance compensation element 7 can preferably be inserted into the wall opening 31a of the first wall 31 from outside, i.e., from outside the frame interface 3, in particular be clipped-in by the sealing lips 72a by means of a minor form fit.

[0101] Additionally, the screw connection of the through-bolt 5 on the second wall 32 in the first exemplary embodiment is formed by means of a nut 51. The through-bolt 5 is in this case screwed into the nut 51 on the second wall 32. The nut 51 can preferably be formed from steel, as preferably also the through-bolt 5, in order to enable a particularly firm screw connection with high torque.

[0102] The nut 51 is arranged in a torsion-proof manner in a recess 32b of the second wall 32. Preferably, the recess 32b is an external radial expansion of a circular second wall opening 32c penetrating through the second wall 32. As can be seen in FIG. 4, the recess 32b comprises two opposite flat portions 32d, i.e., two straight and parallel walls arranged in the tangential direction. The nut 51 has a corresponding geometry with two opposite flat portions 51a. The flat portions 32d, 51a cause the nut 51 in the second wall 32 to not be able to twist, for example as the through-bolt 5 is screwed in, which enables a particularly simple and fast assembly of the drive assembly 1.

[0103] Moreover, the nut 51 is T-shaped in a sectional view. As a result, a maximum thread length can be provided with optimal compactness of the entire drive assembly 1 in order to enable a firm and reliable screw connection with the through-bolt 5.

[0104] FIG. 5 shows a perspective detailed view of a tolerance compensation element 7 of a drive assembly 1 according to a second exemplary embodiment of the present invention. The second exemplary embodiment substantially corresponds to the first exemplary embodiment of FIGS. 1 to 4, with the difference that the sliding bearing bushing 71 of the tolerance compensation element 7 has an alternative design. The sliding bearing bushing 71 is shown in the perspective view of FIG. 5.

[0105] The sliding bearing bushing 71 comprises a longitudinal slot 77, which fully penetrates through the substantially hollow cylindrical sliding bearing bushing 71 in the axial direction and in the radial direction. The longitudinal slot 77 is arranged obliquely with respect to a longitudinal axis 70 of the sliding bearing bushing 71, i.e., it extends along a line which, in a radial projection onto a plane of the longitudinal axis 70, is arranged at an angle of preferably at least 5°, preferably at most 45°, to the longitudinal axis 70. Optimal mechanical support around the entire circumference of the sliding bearing bushing 71 can thereby be provided since, for example, there is no or only a slight interruption of the projected support surface between the bolt head 53 and the first wall 31. This may, for example, enable better coaxial positioning accuracy of the drive unit 2 relative to the frame interface 3.

[0106] The sliding bearing bushing 71 of FIG. 5 also comprises a respective detent lug 78 at each axial end on the outer circumference. The detent lug 78 is designed as an element protruding from an outer circumference of the sliding bearing bushing 71 and brings about a stronger form fit with the first wall 31 (also compare FIG. 3 in this regard). As can be seen in FIG. 5, one of the two illustrated detent lugs 78 is respectively directly adjacent to the longitudinal slot 77, wherein the two detent lugs 78 are arranged on opposite sides of the longitudinal slot 77 with respect to the circumferential direction. Each of the two detent lugs 78 extends only over a portion of the circumference of the sliding bearing bushing 71. Preferably, still further detent lugs 78 (not shown) may be provided distributed around the circumference of the sliding bearing bushing 71.

[0107] In addition, at each axial end, the sliding bearing bushing 71 of FIG. 5 comprises a plurality of recesses 79 distributed around the circumference, which recesses are substantially U-shaped and fully penetrate through the sliding bearing bushing 71 in the radial direction. By means of the recesses 79, more material of the damping element 72 that connects the layer of the damping element 72 that is located at the outer circumference of the sliding bearing bushing 71 to the radially inner layer can be available. As a result, an optimal interconnection of the sliding bearing bushing 71 and the damping element 72 can be produced.

[0108] The interconnection of the sliding bearing bushing 71 and the damping element 72 is further optimized by shoulders 71b at the inner circumference of sliding bearing bushing 71. The shoulders 71b are provided as enlargements of the inner diameter of the sliding bearing bushing 71 starting from the sliding surface 71a. That is to say, the radially inner region of the damping element 72 may be arranged in the shoulders 71b, of which one is respectively located at an axial end of the sliding bearing bushing 71.

[0109] FIG. 6 shows a sectional view of a drive assembly 1 according to a third exemplary embodiment of the present invention. The third exemplary embodiment substantially corresponds to the first exemplary embodiment of FIGS. 1 to 4, with the difference that the damping element 45 is arranged only on the flange 44 of the respective sleeve 41, 42. That is to say, the damping element 45 is respectively disk-shaped and arranged exclusively between the side of the flange 44 that faces the drive unit 2 and of the drive unit 2.

[0110] FIG. 7 shows a sectional view of a drive assembly 1 according to a fourth exemplary embodiment of the present invention. The fourth exemplary embodiment substantially corresponds to the first exemplary embodiment of FIGS. 1 to 4, with the difference that instead of a tolerance compensation element, a retaining element 55 is provided on the first wall 31. In contrast to the tolerance compensation element of FIGS. 1 to 4, the retaining element 55 brings about an axially immovable mounting of the bolt head 53. Moreover, the retaining element 55 brings about a fixation of the bolt head 53 on the first wall 31 in the radial direction completely without play.

[0111] The retaining element 55 is designed as a nut that can be screwed into an internal thread 31f of the wall opening 31a of the first wall 31. The retaining element 55 comprises a retaining opening 55c in which the bolt head 53 of the through-bolt 5 is held. The retaining opening 55c is designed to widen conically toward the second wall 32.

[0112] Additionally, the bolt head 53 comprises a conical lateral surface 53b corresponding to the conical geometry of the retaining opening 55c. That is to say, the bolt head 53, specifically its lateral surface 53b, is designed to taper toward the first wall 31. The corresponding cone angles of the retaining opening 55c and of the lateral surface 53b are identical.

[0113] During the assembly of the drive assembly 1 of FIG. 7, analogously to the drive assembly 1 of FIGS. 1 to 4, the clamping to the second wall 32, i.e., the screw connection of the drive unit 2 to the second wall 32 by means of the through-bolt 5, is produced first. Subsequently, the retaining element 55 can then be screwed until additional clamping of the bolt head 53 in the direction of the second wall 32 takes place. As a result of the conical surfaces of the retaining opening 55c and the lateral surface 53b, the bolt head 53 is centered in the radial direction in the wall opening 31a so that radial clearance is reduced to zero. In particular, a bolt axis 50 is thus exactly oriented coaxially with an opening axis 37 on which the two wall openings 31a, 32c are located.

[0114] The fastening by means of the retaining element 55 offers the additional advantage that high tolerances on the first wall 31 can also be easily and effectively compensated.

[0115] FIG. 8 shows a sectional view of a drive assembly 1 according to a fifth exemplary embodiment of the present invention. The fifth exemplary embodiment substantially corresponds to the fourth exemplary embodiment of FIG. 7, with the difference of an alternative design of the retaining element 55 and of the bolt head 53. In the fifth exemplary embodiment of FIG. 8, the screw connection is provided by means of internal thread and external thread 53c between the bolt head 53 and the retaining element 55. Specifically, the retaining element 55 is screwed onto an external thread 53c of the bolt head 53.

[0116] Furthermore, in the fifth exemplary embodiment of FIG. 8, an outer lateral surface 55b of the retaining element 55 is conically tapered toward the second wall 32. Moreover, an inner lateral surface of the wall opening 31a is conically tapered toward the second wall 32. The cone angles of the two lateral surfaces are identical. This results in substantially the same effect of the radial centering of the bolt head 53 to the wall opening 31a as in the fourth exemplary embodiment of FIG. 7, with the difference that the retaining element 55 screwed to the bolt head 53 is additionally likewise centered. In contrast to the fourth exemplary embodiment of FIG. 7, in the fifth exemplary embodiment, opposing force initiation on the through-bolt 5 takes place through the centering by means of the retaining element 5.

[0117] FIG. 9 shows a detail of a drive assembly 1 according to a sixth exemplary embodiment of the present invention. The sixth exemplary embodiment substantially corresponds to the first exemplary embodiment of FIGS. 1 to 4, with the difference of an alternative sleeve 41, 42.

[0118] Only one of the two sleeves 41, 42 is shown in FIG. 9, wherein the two sleeves 41, 42 are preferably designed identically. The sleeve 41 is shown in a perspective view in FIG. 10.

[0119] The sleeve 41 comprises a shank 43 and a flange 44. The shank 43 is inserted into the through-hole 20 of the drive unit 2. The flange 44 is provided for abutment against an inner side of the second wall 32 of the frame interface 3 (cf., e.g., FIG. 2A). The flange 44 of the sleeve 41 comprises a plurality of protruding form fit elements 41c on the side assigned to the wall 32. Preferably, the form fit elements 41c are arranged in one or more circles that are concentric with the through-opening of the sleeve 41, preferably in two circles as shown in FIG. 9.

[0120] A single form fit element 41c of the sleeve 41 of FIG. 9 is shown in a detailed sectional view in FIG. 10. Each form fit element 41c comprises a pyramid 41d protruding from a surface 41f of the flange 44. Alternatively, each form fit element 41c may also preferably comprise a protruding cone. The pyramid 41d is formed as a straight pyramid and has an opening angle 41k of preferably less than 60°. In this case, the pyramids 41d have the effect that they are pressed into the surface of the wall 32, i.e., plastically deform the wall, as the sleeve 41 is screwed to the wall 32. This produces a micro form fit between the sleeve 41 and the wall 32 in a plane perpendicular to the screw axis, which can enable a particularly firm connection of the drive unit 2 and the frame interface 3 to one another. Slippage of the drive unit 2 relative to the frame interface 3 can thus be reliably prevented.

[0121] In addition to the pyramid 41d, each form fit element 41c comprises a respective depression 41e, which is formed on an outer circumference of the pyramid 41d and in the surface 41f of the flange 44. The depression 41e can, for example, receive material of the wall 32 that is displaced by the penetration of the pyramid 41d into the wall 32, so that the wall 32 and the flange 44 can reliably rest precisely planarly on one another.

[0122] For example, a respective separate depression 51e partially or completely surrounding the pyramid 41d may be provided per pyramid 41d. Alternatively, a single depression 41e can preferably be formed in the surface 41f of the flange 44, the pyramids 41d being arranged on the radial inner side and/or outer side of said depression.

[0123] FIG. 11 shows a detailed sectional view of a drive assembly 1 according to a seventh exemplary embodiment of the present invention. In FIG. 11, only one of the sleeves 41, 42 is shown, namely the sleeve 42 on the side of the second wall 32.

[0124] Preferably, the first sleeve 41 on the first wall 31 is designed identically. The seventh exemplary embodiment substantially corresponds to the first exemplary embodiment of FIGS. 1 to 4, with the difference of an alternative design of the sleeve 42 in the region of the flange 44. At a radially outer end of the flange 44, the sleeve 42 comprises a taper 41g on the side of the flange 44 that faces the shank 43. The taper 41g is designed in such a way that a difference between the maximum thickness 41h and a minimum thickness 41i of the flange 44 corresponds to at least 50%, preferably at most 150%, of a wall thickness 43h of the shank 43 of the sleeve 42. In this respect, the thicknesses along a direction parallel to a longitudinal axis of the sleeve 42 are considered.

[0125] The damping element 45 is designed to compensate for the taper 41g of the flange 44. Additionally, at a radially outermost end, the damping element 45 comprises a thickening 42g. As a result, a particularly thick damping element 42 is present at the radially outer end of the flange 44. This has an advantageous effect on an optimal seal between the sleeve 42 and the drive unit 2.

[0126] This seal is furthermore supported by a protruding annular rib 2g of the drive unit 2, which is provided in the seventh exemplary embodiment as shown in FIG. 12. The protruding annular rib 2g has a trapezoidal cross-section and is arranged concentrically with the through-hole 20 of the drive unit 2. In the pressed-in state of the sleeve 42 into the through-hole 20, the protruding annular rib 2g and the taper 41g of the sleeve 42 are located on the same radius with respect to the drilling axis 20g of the through-hole 20. As a result, the protruding annular rib 2g dips into the soft zone of the damping element 45 in the region of the taper 41g when the sleeve 42 and the drive unit 2 are pressed against one another in the fully screwed state. As a result of the elasticity of the damping element 45, an optimal seal can thus be provided at the drive unit 2.

[0127] FIG. 13 shows a sectional view of a drive assembly 1 according to an eighth exemplary embodiment of the present invention. The eighth exemplary embodiment substantially corresponds to the first exemplary embodiment of FIGS. 1 to 4, with the difference that the drive unit 2 is indirectly screwed to the frame interface 3. Specifically, the two walls 31, 32 to which the drive unit 2 is screwed are designed as separate components from the frame interface 3. The walls 31, 32 may be designed as retaining plates, for example. In this case, the walls 31, 32 can be connected to frame walls 31e, 32e of the frame interface 3 by means of additional screw connections 30 and/or weld connections (not shown). As a result, a particularly high flexibility of the drive assembly 1 can be provided.

[0128] FIG. 14 shows a sectional view of a drive assembly 1 according to a ninth exemplary embodiment of the present invention. The ninth exemplary embodiment substantially corresponds to the first exemplary embodiment of FIGS. 1 to 4, with the difference of an alternative design of the sleeves 41, 42. In the ninth exemplary embodiment of FIG. 14, the two sleeves 41, 42 are designed as shortened metal sleeves that particularly simple and cost-effective to produce. The sleeves 41, 42 are designed in such a way that they do not contact one another within the through-hole 20. Moreover, the two sleeves 41, 42 have a short axial length 41g, which is, for example, smaller than an inner diameter of the through-hole 20. As a result, material can be saved and simple pressing of the sleeves 41, 42 into the through-hole 20 is also enabled since there is only a small press length. The drive assembly 1 of the ninth exemplary embodiment thus enables a particularly simple and cost-effective construction.

[0129] FIG. 15 shows a sectional view of a drive assembly 1 according to a tenth exemplary embodiment of the present invention. The tenth exemplary embodiment substantially corresponds to the seventh exemplary embodiment of FIGS. 11 and 12, with the difference that alternative sleeves 41, 42 are used.

[0130] Specifically, the flanges 44 of the sleeves 41, 42 are thicker in the tenth exemplary embodiment of FIG. 15 than in the seventh exemplary embodiment. Specifically, the thickness 41h of the flanges 44 in the tenth exemplary embodiment is a multiple of, preferably at least three times, a wall thickness 43h of the corresponding shank 43 of the respective sleeve 41, 42. As a result, an overall width 1h of the drive assembly 1 can be larger compared to the seventh exemplary embodiment, in which the thickness 41h of the flange 44 is approximately equal to the wall thickness 43h of the shank 43, for example. The tenth exemplary embodiment of FIG. 15 thus illustrates that through changes in the sleeves 41, 42, it is possible to adapt the drive assembly 1 to various vehicles 100 in a particularly simple and cost-effective manner.

[0131] FIG. 16 shows a sectional view of a drive assembly 1 according to an eleventh exemplary embodiment of the present invention. The eleventh exemplary embodiment substantially corresponds to the first exemplary embodiment of FIGS. 1 to 4, with the difference of an alternative design of the floating bearing on the first wall 31. In the eleventh exemplary embodiment of FIG. 16, the through-bolt 5 and the tolerance compensation element 7 are mounted together axially movably relative to the first wall 31. In this case, in contrast to the first exemplary embodiment, not the bolt head 53 but rather a bolt shank 53d of the through-bolt 5 is arranged within the tolerance compensation element 7. In the eleventh exemplary embodiment, the through-bolt 5 additionally clamps the tolerance compensation element 7 against the first sleeve 41. The through-bolt 5 and the tolerance compensation element 7 can thus slide together in the wall opening 31a of the first wall 31. The wall opening 31a also has an enlarged diameter 31b on the outside so that the bolt head 53 can be arranged partially within the wall opening 31a. Alternatively, the bolt head 53 can also be arranged entirely outside the wall opening 31a.

[0132] FIG. 17 shows a detailed sectional view of a drive assembly 1 according to a twelfth exemplary embodiment of the present invention. The twelfth exemplary embodiment substantially corresponds to the seventh exemplary embodiment of FIGS. 11 and 12, with the difference of an alternative design of the damping element 45. In the twelfth exemplary embodiment of FIG. 17, the damping element 45 comprises a sealing bead 45a at an axial end of the sleeve 41 that is opposite the flange 44. The sealing bead 45a protrudes in the axial direction from an end face 43c of the shank 43 of the sleeve 41. Moreover, the sealing bead 45a protrudes radially outward from the damping element 45.

[0133] The axial protrusion 45f of the sealing bead 45a is preferably at least 20% of the wall thickness 43h of the shank 43. Moreover, the radial protrusion 45g is preferably at least 30% of the wall thickness 43h of the shank 43.

[0134] The sealing bead 45a on the damping elements 45 of the sleeves 41, 42 brings about a particularly reliable seal against ingress of fluid. This is achieved by pressing each seal bead 45a both axially and radially, as shown in FIG. 18. By clamping the sleeves 41, 42 in the axial direction against one another, the two sealing beads 45a are axially pressed against one another. For example, by a radial interference of the sealing bead 45a with respect to an inner circumference 20g of the through-hole 20, each sealing bead 45a can additionally be pressed against the inner circumference 20g of the through-hole 20 in the radial direction. A reliable seal by means of the sealing bead 45a thus results radially outside the shanks 43 of the sleeves 41, 42 in the plane of the contacting end faces 43c of the sleeves 41, 42.

[0135] FIG. 19 shows a detailed sectional view of a drive assembly 1 according to a thirteenth exemplary embodiment of the present invention. The thirteenth exemplary embodiment substantially corresponds to the twelfth exemplary embodiment of FIGS. 17 and 18, with the difference of an alternative design of the flange 44 of the sleeves 41, 42. In the thirteenth exemplary embodiment of FIG. 19, the flange 44 of the sleeve 42 is formed in two parts and comprises a flange base body 44a and an insert ring 44b. The flange base body 44a is formed together with the shank 43 of the sleeve 42 as a one-piece component. The insert ring 44a is formed concentrically with the sleeve opening of the sleeve 42 and is arranged in a groove 44g of the flange base body 44a. The insert ring 44b is in this case held in the groove 44g by means of an axial form fit 44f. The axial form fit 44f can, for example, be produced by peening, i.e., forming, sub-regions of the flange base body 44a. In the thirteenth exemplary embodiment, the form fit elements 41c are arranged exclusively on the insert ring 44a and are formed as a part thereof.

[0136] The insert ring 44b is formed from a hardened steel that has a significantly higher hardness than the material of the flange base body 44a and the shank 43. This ensures a particularly high degree of robustness and thus permanently reliable function of the form fit elements 41c. Moreover, the two-part design of the flange 44 enables the flange base body 44a and the shank 43 to be formed from a steel that is well-suited for cold forming. As a result, the sleeves 41, 42 can be produced in a particularly simple and cost-effective manner.