DE19854798C1 - Drive shaft for power train in vehicle - Google Patents

Abstract

A drive shaft for a power train in a vehicle links the transmission with the rear axle drive with a single lightweight shaft made of plastic or fibre reinforced material, with a similar elastic modulus as a steel shaft. The spring loaded couplings (4) counteract any lateral displacement of the shaft and provide a deep pass filter effect for vibrations. The resonant frequency of the shaft is higher than the transmission vibrations, which are damped by the filter.

Description

The invention relates to a drive train for motor vehicles, especially passenger cars according to the preamble of the An saying 1.

The design of the drive train in the aforementioned manner is for Motor vehicles, especially larger, more comfortable people motor vehicles a standard design (see for example: DE book "Everything about the Mercedes-Benz E-Class", 2nd edition, ed via: Daimler-Benz AG, ISBN 3-9804457-3-9, page 98). At ange driven rear axle, the engine and transmission are on the front arranges and with the axle gear of the rear axle over a Ge steering shaft connected. This structure of the drive train is conditional for the cardan shaft, bridging a considerable distance, for the Ge made of steel and trained as a pipe steering shaft a subdivision for vibration reasons and additional storage in the central vehicle area nope tig, because otherwise the first natural bending frequency of the articulated shaft le with their rotational frequency in the range of the operating speed would collapse, making vibrational breaks almost inevitable would do. By dividing and shortening the free PTO shaft range, the natural bending frequency can be in  Raise non-critical areas. This configuration has un constructional, cost and noise aspects, also night-time le. Construction is in addition to the drive shaft side (Engine / gearbox) as well as to the axle side (rear axle gearbox) elastic connection of the cardan shaft, via elastic coupling lungs in the form of articular discs, in the median Cardan shaft area a subdivision with storage and articulated ger connection via a universal joint required, the spatial as well as additional expense from a cost perspective points. In addition, the storage is in the middle of the floor area the vehicle is also not uncritical in terms of vibration technology and makes additional damping measures if necessary the construction required.

Elastic joint connections are in the transition to the cardan shaft also known elsewhere, for example from DE 37 02 800 C2, DE 91 10 049 U1 and DE 42 21 417 C2.

Also for relatively long cardan shafts, which as a one-piece Cardan shafts could be used, can be in uncritical loading rich first bending natural frequencies raised by 150 Hz rea lize, and that for cardan shafts from specifically lighter Material as steel with a high elasticity comparable to steel module, such as those used as composite shafts from DE- Book, "CV drive shafts for passenger cars", publisher modern industry, 1998, volume 170, pages 34-37, in particular Fig. 33, embodiment e are known. Because of Weight saving as well as for reasons of space saving and to simplify the structure would be such a one-piece joint prefer shafts in the drive train. It does not apply to one  such a one-piece propeller shaft arrangement but the low-pass Filter effect of the two-part propeller shaft arrangement through which motor-induced bending vibrations in the range greater than 25 to 30 Hz are decoupled so that the rear axle is vibration-sensitive nisch is relieved. This reduces the level of noise comfort Measure that is considered unacceptable and that the one So far practically prevent set of such one-piece propeller shafts has.

The invention aims to build a drive train of the type mentioned above, in which without Vibration-related disadvantages on additional storage and support of the cardan shaft in its longitudinal center Area can be dispensed with.

According to the invention, this is achieved by the features of claim 1 reached. A one-piece joint is used wave of high natural bending frequency, d. H. a natural bending frequency first order, which is at least about 30% above the rotational frequency at operating speed of the internal combustion engine, and preferably in is on the order of ≧ 150 Hz. This cardan shaft is on the drive source side via a cardan shaft connection tied towards the aligned extension of the PTO shaft between the drive source side and the axis side Connection is elastically supported as a starting position. This elastic support is designed so that the Articulated connection from this starting position in the bend vibration level of the cardan shaft depending on the force of the mass is pivotable. The articulation is such designed that with axial displacement of the drive sources side linkage for axle-side linkage a transverse offset the articulation is possible. This looks elastic centering support force, which is dependent from the spring rate of the elastic support corresponding deflection and that in relation to the Mass of the propeller shaft is dimensioned such that the Articulated connection based on the bending vibrations of the PTO shaft forms a low pass. With that solution according to the invention despite the one-piece propeller shaft  Transmission of motor-excited bending vibrations to the Rear axle at least largely avoided that the front parts of a one-piece propeller shaft in terms of construction volume and construction costs can be used. In addition, the Use of cardan shafts using material technologies such as B. fiber reinforced plastics weight savings, and a lightweight design concept made possible by this is without disadvantages especially in the area of noise development feasible.

Within the scope of the invention, an articulated connection can be made with Low pass effect using an inner body and realize a swivel joint having an outer body, at the inner and outer body are rotatably connected and based on a common center point across the shoot direction towards each other and towards the The center position of the joint is supported against one another in a springy manner are. The centering support can be both axial as well as radial support between the inside and Realize outer body, changing between each other axially overlapping parts of the inner body and Outer body, the resilient support means are arranged can. With axial support, the resilient Support means preferably between the outer circumference of the Outer body and the inner circumference of a collar arranged be the part of the inner body the outer body radially overlaps axially. When designing a Such swivel can largely be known homogeneous swivel joints can be used.  

It proves expedient to drive the inner body source-side connection and the outer body to assign the universal joint connection of the swivel joint. Regarding the PTO connection of the External body, it proves to be useful, this one assign radial ring web that engages over the inner body and via which the connection to the cardan shaft is made. A such an arrangement enables by pivoting the rotation joint and the axial offset of the center of the joint Cardan joint to the swivel axis offset between the drive-side articulation of the articulation and the axle-side linkage to the cardan shaft, this Axis offset depends on the force of the mass and against the elastic support between inner body and outer body of the swivel joint. The size of the axial offset between the center of the swivel and the center of the universal joint as the double forming the joint connection joint to the size of the lever arm under which the swivel joint acting towards its centered location Supporting force acts, enables within the scope of the Invention solution according to the realization of translations relationships in the relationship between mass force and support force to influence the vibration behavior and the Effect as a low-pass filter, due to the motor-excited bending vibrations decoupled and the rear axle vibrationally is relieved. Also drive side Self-excitation of the drive train, such as Un balance, which arise in the area of the gearbox, from the rear axle isolated.  

In the context of the invention, the articulated connection can be advantageous also by means of a double joint encompassing two universal joints be formed, with respect to their joint centers axial, d. H. in the longitudinal direction of the drive train against mutually offset universal joints on theirs to each other aligned position are elastically biased. This elastic Bias can be achieved by the Universal joints are supported axially against one another, for example, by radially over the universal joints gripping, axially extending and against the Ge screws supporting the steering connection of the shaft parts feather. The corresponding shaft parts, or those with them Connected joint parts can be radial have covenants. In the embodiment of this principle it is also possible, that between the shaft-side joint forks to assign a radial collar to the horizontal intermediate joint carrier and the axially elastic support based on the respective shaft-side supports against this radial to make bund.

Another embodiment of an articulated ver Binding can be created according to the invention in that two axially spaced elastic joint disks provided , one of which is on the drive source side and the other is arranged on the axis and each over Connection stars with the respective shaft side as well are interconnected, the connecting pin of shaft-side connection star preferably coaxial with each other lie and offset in the circumferential direction to the connecting pin  of the distance between the joint discs and the distance between these bridging connection star.

This connecting star lying between the joint discs preferably has a central, exposed guide sleeve on the joint disks, which in turn have radial support arms from the connecting pins this star is born and in which each other centrally located adjacent shaft ends Guide pins are kept elastic. Through this structure is functionally using a double joint the corresponding one is reproduced from joint disks Has low pass function.

Further details and features of the invention emerge from the claims. Furthermore, the invention with others Details explained using the exemplary embodiments. It demonstrate:

Fig. 1 is a schematic representation of a drive train according to the invention in its basic sätzlichen training,

Fig. 2 shows a first embodiment of the drive-source side provided in the transition to the hinge shaft, hinge connection formed by a double joint, said double joint is constituted by a constant velocity joint and a downstream universal joint, shown partly in section,

Fig. 3 + 4 further embodiments of a hinge formed as a double hinge joint wherein the double hinge is formed by two universal joints, shown partly in section,

Fig. 5 shows a joint connection according to the invention, in which a double joint is functionally represented by two axially spaced joint disks, partially cut, and

Fig. 6 + 7 sectional views corresponding to the section lines VI-VI and VII-VII through the joint connection according to FIG. 5 to illustrate the connection between the joint disks and the connection of the joint disks on the respective drive source-side or axle-side shafts.

Fig. 1 shows schematically the drive train of a passenger car, not shown, in which, based on the forward driving direction F, at least the drive source, in particular an internal combustion engine, but preferably a drive unit 1 consisting of an internal combustion engine, clutch and gearbox, is assigned to the front axle and is assigned via a PTO shaft 2 is connected to the driven rear axle, which is symbolized here by the rear axle gear 3 . Deviating from what is shown, it is also possible to only provide the internal combustion engine from the front and to assign the gearbox to the rear axle, even if the first-described structure with internal combustion engine and gear unit comprising drive unit 1 is a preferred embodiment.

The PTO shaft 2 spans the distance between the drive unit 2 and the rear axle 3 without intermediate storage and is formed in one piece, the connection of the PTO shaft 2 to the drive unit 1 , ie the drive source side connection via an articulated connection 4 , which is an elastokinematic mounting for the PTO shaft 2 forms, while the connection of the PTO shaft 2 to the rear axle gear 3 is carried out in the usual way via an articulated disk 5 , via which the PTO shaft 2 is aligned with the input shaft 6 of the rear axle gear 3 assigned to the rear axle.

The articulated connection 4 in the transition between the articulated shaft 2 and the output shaft 7 on the drive source side of the transmission belonging to the drive unit 1 is formed by a double articulation, as will be explained in more detail in various configurations with reference to the following figures, and that due to its aligned extension of the articulated shaft 2 between the drive source-side connection (output shaft 7 ) and the axle-side connection (input shaft 6 ) corresponding initial position is elastically biased, but can be deflected depending on the force of gravity from this aligned starting position. In connection with a propeller shaft 2 , which is designed within the scope of the invention as a one-piece propeller shaft with a high natural bending frequency, in particular, which is not apparent from the drawing, as a lightweight shaft, for B. consists of fiber-reinforced plastic, allows the fiction, contemporary design of the joint 4 by ent speaking coordination of their elasticity to the relatively small mass of the propeller shaft 2 in the bearing area formed by the joint 4 for the joint shaft 2, a natural frequency of the order of about 25 Hz and thus a design with a low-pass filter effect. The low-pass filter decouples motor-excited bending vibrations in the order of magnitude of ≧ 25 Hz, so that the rear axle 3 is relieved of vibrations. Self-excitations of the drive train, such as. B. unbalances, which arise in the transmission-side area, also isolated from the rear axle 3 .

The propeller shaft 2 in its design as a fiber-reinforced plastic shaft can meet the demand for bending natural frequencies of the first order with ≧ 150 Hz given the propeller shaft lengths and propeller shaft diameters given within the framework of the described construction of the drive train, so that a sufficient distance of the shaft rotational frequency can be achieved, which at operating speeds of 6000 revolutions per minute is 100 Hz. The combination according to the invention of a cardan shaft 2 in lightweight construction technology in connection with a joint connection 4 , which, as the drive-side bearing of the cardan shaft 2, has the effect of a low-pass filter with a cut-off frequency of the order of 25 Hz, enables the isolation of engine-side vibrations from the rear axle and thus the Use of the advantages of the lightweight construction concept of a cardan shaft without any noise-related disadvantages.

For articulation 4 2 a first embodiment is shown in Fig., The hinge connection is formed by a double joint comprising a homokinetic joint 8, referred to as a swivel joint, and a universal joint. 9 The swivel joint 8 is arranged adjacent to the drive unit 1 , and the universal joint 9 connects to the propeller shaft 2 . The joint center points designated 10 and 11 are in the longitudinal extension of the drive train, that is to say axially offset from one another, and they are in the structurally predetermined starting position in alignment with the drive source-side and axis-side connection, formed by the output shaft 7 and the input shaft 6 in accordance with the basic structure shown in FIG. 1 .

The trained as a homokinetic joint 8 includes, as can be seen from the partial sectional view of FIG. 2, an inner body 12 and an outer body 13 , which have mutually facing spherical guide surfaces 14 and 15 and connected to each other in the form of balls 16 torque transmitting connected with each other are. The inner body 12 has on its drive-side end face a radial annular web 17 , to which an annular collar 18 adjoins radially on the outside, which overlaps the outer body 13 axially at a radial distance. The inner body 12 thus forms with its annular web 17 and the annular collar 18 a cross-sectionally U-shaped annular channel which is open towards the driven side and into which the outer body 13 protrudes from the driven side, which in turn projects a radially inwardly projecting annular web 19 carries, which ends in the axially extending against the propeller shaft 2 joint fork 20 , which in turn is connected in a known manner for universal joints via an articulated star with a second joint fork 21 of the universal joint 9, which is assigned to the propeller shaft 2 .

Between the cylindrical outer circumference of the outer body 13 and the annular collar 18 of the inner body 12 which extends axially at a radial distance there is a compression spring 22 which is designed here as a helical spring and which is clamped between radial support collars 23 and 24 of the inner body 12 and the outer body 13 , of which the support collar 23 is provided on the free end of the annular collar 18 of the inner body 12 projecting radially inwards, while the supporting collar 24 is assigned to the end of the outer body 13 adjacent to the annular web 17 of the inner body 12 and extends radially outward. The compression spring 22 is supported around the outer body 13 between the support collars 23 and 24 . According to the arrangement of the compression spring 22 , the inner body 12 and the outer body 13 are aligned via the compression spring 22 to a central position of the rotary joint 8 , so they are quasi coaxial, but are from this aligned position by bending forces acting perpendicular to the axis of the drive shaft 2 , as they are known as the mass forces of PTO shaft 2 are effective, deflectable in that the rotary joint 8 is pivoted against the force of the compression spring 22 from its central position, with the result that there is an axial offset for the center 11 of the universal joint 9 which is axially offset from the center 10 of the rotary joint 8 , corresponding to the radial displacement of the joint center point 11 of the universal joint 9, which occurs due to the direction of the respective mass forces against the force of the compression spring 22 . Within the scope of the invention, different arrangements of the compression spring 22 are also possible, such as a division of the compression spring into a plurality of individual springs which are arranged distributed over the circumference, or also radial spring arrangements and supports formed by elastomeric materials which have an axial, radial or combined axial / radial Form support between the inner ring and outer ring, even if the solution shown forms a preferred solution.

Due to the comparatively low mass of the one-piece, fiber-reinforced plastic joint shaft 2 used here compared to steel cardan shafts and the elasticity in the bearing area, a natural frequency of the order of 25 Hz is formed, and the bearing area formed by the swivel joint also forms the PTO shaft 2 is a low-pass filter, with the result that the engine-side vibrations are isolated from the rear axle via this natural frequency. The solution according to the invention thus brings about a saving in weight and construction volume without known adverse effects on the noise behavior compared to known two-part designs.

The embodiments according to FIGS. 3 and 4 show articulated joints 4 the same basic structure, wherein (Fig. 3) (FIG. 4) is in both cases a double joint 30 and 31 use. The double joint 30 of FIG. 3 consists of two universal joints 32 and 33. The universal joints 32 , 33 each have an articulated fork 34 and 35 assigned to the adjoining shaft part, that is to say the output shaft 7 on the one hand and the articulated shaft 2 on the other hand, and these articulated forks 34 and 35 each have an articulated star 36 and 37 with the corresponding forks 38 and 39 connected, which in turn are assigned to an intermediate support 40 as a connecting link between the joint forks 34 and 35 . The respective center points of the joint are designated 41 and 42 and are axially spaced apart in the direction of extension of the drive. The two universal joints 32 and 33 of the double joint 30 are enclosed with play by an axially extending coil spring 43 , the forks 34 and 35 associated supports 44 and 45 associated with the respective joint associated with the further shafts. The supports 44 , 45 are bell-shaped here, so that they have radial support surfaces 46 and 47 for the respective spring ends and axially extending sections 48-51 extending therefrom . Of these, the connection to the respective joint fork 34 and 35 is made via the radially inner sections 48 and 49 extending in the direction of the respective connecting shafts and the spring 43 is shielded radially via the radially outer sections 50 and 51 extending in the opposite direction outside, these sections 50 , 51 ending axially at a distance from one another and possibly forming a guide for partial sections of the spring 43 .

The basic structure of the articulated connection 4 according to FIG. 4 corresponds to that according to FIG. 3. Therefore, largely the same reference numerals are used. Instead of a single spring 43 in FIG. 3, two springs 53 , 54 are provided in the design according to FIG. 4, and these springs are supported on the one hand, as in FIG. 3, against radial support surfaces 46 , 47 of supports 44 , 45 from between which there is a support 55 which is assigned to the intermediate carrier 56 , which has a radial flange forming the support 55 in the longitudinally central region lying between its articulated forks 38 , 39 .

In both embodiments, that is, in the embodiment according to Fig. 3 as well as in the embodiment of FIG. 4, the joint 4 is thus formed of a double hinge 30, 31, analogous to the embodiment according to Fig. 2 in the direction of its the central position of Joint corresponding, aligned alignment in the drive train is spring-loaded, but can also be deflected in pivoting positions depending on the force of gravity, in which there is an axial offset between the drive-side and axle-side connection.

A further embodiment of a power source side bearing unit serving for the propeller shaft 2 articulated joint 4, Figs. 5 to 7, in which case the hinge joint 4, but resilient using flexible disks 60, built 61 is spaced axially in the direction of extension of the drive train to each other between the driving sources side Output shaft 7 and the axis-side input shaft 6 are arranged. For the sake of simplicity, the respective shaft end is shown here as a unit formed in one piece with a connecting flange, but this is not essential within the scope of the invention.

The connection flanges 62 , 63 together with connection pins 64 , 65 carried by them each form connection stars 66 , 67 , the schematic sectional views according to FIGS. 6 and 7 illustrating that the connection flanges 62 , 63 can be triangular in shape, with connection pins 64 assigned to their corner regions or 65 , the connecting pins 64 or 65 being located in the corner points of isosceles triangles, the bisector of which intersect at a point which lies on the respective shaft axis 6 or 7 . The connecting flanges 62 and 63 also each carry a central guide pin 68 , 69 which extends in the same direction and parallel to the connecting pin 62 , 63 and which is aligned with the respective shaft axis.

The central guide pins 68 , 69 engage axially in a guide sleeve 70 which extends through to the joint disks 60 , 61 and against which the central guide pins 68 and 69 are supported via elastic intermediate sleeves 71 , 72 . Via the guide sleeve 70 , with the intermediary of the elastic intermediate sleeves 71 and 72 and the guide pins 68 and 69, there is an elastic basic alignment of the drive source-side and the axle-side shaft sections 7 and 6, respectively, in an aligned position.

The guide sleeve 70 in turn forms the center of a further connection star 73 , which has connection pins 74 , via which the axially spaced articulated disks 60 , 61 are connected to one another, the connection pins 74 of the connection star 73 being offset from the connection pins 64 and 65, each 60 ° apart, Connection stars 66 and 67 are arranged standing on a gap, and the connection stars 66 , 67 and 73 each have three connection pins.

In the largely schematic representation according to Fig. 5 to 7, the terminal pins 64, 65 and 74 are each shown as directly into the respective joint plate 60 and 61, engaging parts. In a deviation from this, corresponding receiving sleeves can of course be provided, and it is a further solution within the scope of the invention to assign the flexible disks 60 , 61 to the flexible disks as receptacles for the connecting pins 62 , 63 and / or 74 , so that the reciprocal elastic support can be influenced via the central guide and also via the hardness of the elastic flexible disks and / or the hardness of the additional elastic guides for the connecting pins.

In such a solution, the elastic basic centering takes place via the central guide sleeve 70 and the associated central guide pins 68 and 69 . If vibrational excitations occur due to transverse forces, the joint disks 60 , 61 are axially stressed, that is to say deformed transversely to their plane, and act as a basic spring element due to their inherent elasticity. This results overall in an articulated connection which is comparable in its effects to that of the articulated connections described with the aid of the previous figures and which results in a low-pass filter effect which brings about isolation with respect to the transmission of engine-side vibrations of approximately 25 Hz to the rear axle.

Claims (37)

1.Drivetrain for motor vehicles, in particular passenger cars with axles assigned to two opposite end regions of the vehicle, the drive source lying in the region of the first of these axles and the drive source connecting the drive shaft with the second of these axles, extending in the vehicle longitudinal direction, the drive source side connection of which is designed as an elastic articulated connection , characterized in that the cardan shaft ( 2 ) is designed as a one-piece cardan shaft of high natural bending frequency, that the articulated connection ( 4 ) has a starting position corresponding to the aligned extension of the cardan shaft ( 2 ) between the connection on the drive source side and the axle side (shafts 6 , 7 ) Starting position is supported elastically and from this starting position in the plane of flexural vibration of the universal joint shaft ( 2 ) depending on the force of force, a position can be swung out in which the articulation at the drive source-side articulation connects the joint g ( 4 ) for the axle-side articulation there is an axial offset of the articulations and that the elastically centering supporting force in relation to the mass of the articulated shaft ( 2 ) is dimensioned such that the articulated connection ( 4 ) forms a low pass in relation to the bending vibrations of the articulated shaft ( 2 ) . 2. Drive train according to claim 1, characterized in that the drive shaft ( 2 ) consists of a specifically lighter material than steel with approximately the same modulus of elasticity. 3. Drive train according to claim 1 or 2, characterized in that the drive shaft ( 2 ) is formed from a lightweight material with a high modulus of elasticity. 4. Drive train according to one of the preceding claims, characterized in that the drive shaft ( 2 ) is designed as a plastic hollow shaft. 5. Drive train according to one of the preceding claims, characterized in that the drive shaft ( 2 ) is designed as a composite shaft. 6. Drive train according to claim 5, characterized in that the cardan shaft ( 2 ) is designed as a fiber composite shaft. 7. Drive train according to one or more of the preceding claims, characterized in that the articulated connection ( 4 ) comprises an inner body ( 12 ) and an outer body ( 13 ) having a rotary joint ( 8 ), in the inner body ( 12 ) and outer body ( 13 ) rotatably connected, based on a common center point transverse to the direction of rotation against each other and axially resiliently supported against each other. 8. Drive train according to claim 7, characterized in that resilient support means (compression spring 22 ) are arranged between mutually axially overlapping parts of the inner body ( 12 ) and outer body ( 13 ) of the rotary joint ( 8 ). 9. Drive train according to claim 8, characterized in that the resilient support means are arranged as an axial support between the outer circumference of the outer body ( 13 ) and the inner circumference of an annular collar ( 18 ) which, as part of the inner body ( 12 ), the outer body ( 13 ) radially overlaps axially on the outside. 10. Drive train according to claim 9, characterized in that the annular collar ( 18 ) of the inner body ( 12 ) via a radial annular web ( 17 ) of the inner body ( 12 ) is carried. 11. Drive train according to one of claims 7 to 10, characterized in that the inner body ( 12 ) and the outer body ( 13 ) have mutually facing spherical guide surfaces ( 14 , 15 ). 12. Drive train according to claim 11, characterized in that the inner body ( 12 ) and the outer body ( 13 ) via intermediate transmission elements, in particular balls ( 16 ) are torque-transmitting against each other. 13. Drive train according to one of the preceding claims, characterized in that the rotary joint ( 8 ) is designed as a homogeneous joint. 14. Drive train according to one of the preceding claims, characterized in that the inner body ( 12 ) forms the drive source-side connection of the swivel joint ( 8 ). 15. Drive train according to one of the preceding claims, characterized in that the outer body ( 13 ) forms the joint-shaft connection of the swivel joint ( 8 ). 16. Drive train according to one of the preceding claims, characterized in that the outer body ( 13 ) has a radial annular web ( 19 ) via which the connection to the propeller shaft ( 2 ) takes place. 17. Drive train according to one of the preceding claims, characterized in that the articulated connection ( 4 ) subsequent to the rotary joint ( 8 ) in the transition to the propeller shaft ( 2 ) comprises a universal joint ( 9 ). 18. Drive train according to one of the preceding claims, characterized in that the center of the rotary joint ( 8 ) to the center of the universal joint ( 9 ) in the direction of the drive shaft ( 2 ) is axially offset. 19. Drive train according to one of the preceding claims, characterized in that an articulated fork ( 20 ) of the universal joint ( 9 ) is assigned to the annular web ( 19 ) of the outer body ( 13 ). 20. Drive train according to one or more of the preceding claims, characterized in that the articulated connection ( 4 ) is formed by a double joint (swivel joint 8 , universal joint 9 ) with axially offset center joints ( 10 , 11 ) in the longitudinal direction of the drive train. 21. Drive train according to claim 20, characterized in that the double joint comprises a swivel joint ( 8 ) and a universal joint ( 9 ). 22. Drive train according to claim 20 or 21, characterized in that the rotary joint ( 8 ) is designed as a homogeneous joint. 23. Drive train according to one or more of the preceding claims, characterized in that the swivel joint ( 8 ) is elastically supported on its position corresponding to the aligned position of the drive shaft ( 2 ) between the drive source-side and axle-side connection. 24. Drive train according to claim 20, characterized in that the joint connection ( 4 ) is formed by a two universal joints ( 32 , 33 ) comprising a double joint ( 30 , 31 ). 25. Drive train according to claim 24, characterized in that the two universal joints ( 32 , 33 ) are elastically biased to their aligned position. 26. Drive train according to claim 25, characterized in that the two universal joints ( 32 , 33 ) are axially elastically supported against each other. 27. The drive train according to claim 26, characterized in that the universal joints ( 32 , 33 ) each have an articulated fork ( 34 , 35 ) on the drive source side and on the axle side, and the two articulated forks ( 34 , 35 ) are connected via an intermediate support ( 40 ) forked at both ends are. 28. Drive train according to one or more of claims 25 to 27, characterized in that the drive source-side and axle-side joint forks ( 34 , 35 ) have radial support surfaces ( 46 , 47 ) for the axially flexible support, in particular in the form of a spring ( 43 ) are. 29. Drive train according to claim 28, characterized in that the resilient support is formed by a helical spring ( 43 ) lying between the radial support surfaces ( 46 , 47 ). 30. Drive train according to one or more of claims 25 to 29, characterized in that the intermediate carrier ( 40 ) is assigned a radial flange ( 57 ) lying between its forked ends. 31. Drive train according to claim 30, characterized in that the radial flange ( 57 ) is acted upon axially on both sides by springs, in particular helical springs ( 53 , 54 ) supported against the support surfaces ( 46 , 47 ). 32. Drive train according to one or more of claims 1 to 23, characterized in that the articulated connection ( 4 ) is formed by two axially spaced elastic articulated disks ( 60 , 61 ), one of which is arranged on the drive source side and the other on the axis side and each are connected via connecting stars ( 66 , 67 , 73 ) on the drive source side, axis side and with each other. 33. Drive train according to claim 32, characterized in that the drive source-side and axle-side connection stars ( 66 , 67 ) are coaxial with respect to their connecting pins ( 64 , 65 ). 34. Drive train according to claim 32 or 33, characterized in that the connecting pins ( 74 ) of the connecting star ( 73 ) lying between the articulated disks ( 60 , 61 ) to the connecting pins ( 64 , 65 ) of the connecting stars ( 66 , 67 ) lie on a gap . 35. Drive train according to one of claims 31 to 34, characterized in that the connecting star ( 73 ) lying between the articulated disks ( 60 , 61 ) has a central guide sleeve ( 70 ), in the central guide pin provided on the drive source side and on the axis side ( 68 , 69 ) are kept elastic. 36. Drive train according to claim 35, characterized in that the connecting pins ( 74 ) of the connecting star ( 73 ) lying between the joint disks ( 60 , 61 ) are connected to the guide sleeve ( 70 ) via radial support arms. 37. Drive train according to one of claims 35 or 36, characterized in that the guide sleeve ( 70 ) relative to the joint disks ( 60 , 61 ) is without direct support.