DE19926983A1 - Hydrodynamic torque converter has housing containing turbine wheel with casing and hub, torsional oscillation damper, cover discs and thrust piece - Google Patents

Abstract

The housing (12) contains a turbine wheel (24) pivot mounted on a converter pivot axle. The turbine wheel has a casing (26) and hub (30). A primary and secondary side of a torsional oscillation damper arrangement (40) are joined to the turbine wheel case and turbine wheel hub respectively. Both the primary and secondary sides are rotated on the converter pivot axle against the action of a damper arrangement (82). Two axially spaced apart cover-disc elements (70,72) are positioned on one side; the other side comprises a central disc element positioned axially between the two cover disc elements. At least one of the cover disc elements has a thrust piece (74).

Description

The present invention relates to a hydrodynamic torque ment converter, comprising a housing, an in the housing with respect the turbine wheel, which is rotatable about a converter axis of rotation, which has a turbine wheel shell and a turbine wheel hub, and a torsional vibration damper arrangement, wherein a primary side of the Torsional vibration damper arrangement with the turbine wheel shell is connected and a secondary side of the torsional vibration damper Arrangement is connected to the turbine hub, and wherein the primary side and the secondary side against the action of a damping arrangement are rotatable with respect to each other about the axis of rotation of the transducer, one side two axially spaced from the primary and secondary side and includes firmly connected cover plate elements and the other side of the primary side and secondary side a central disc element comprises the axially between the two cover plate elements Primary side is arranged.

Such a hydrodynamic torque converter is, for example, from known from DE 195 14 411 A1. In this known hydrodynamic Torque converter is the primary side of the torsional vibration damper arrangement in its radially outer region, d. H. in the radially outer area the cover plate elements, by riveting to the turbine wheel shell connected. The secondary side, i.e. H. the central disc element is in their radially inner area, by riveting to the turbine hub bound. The damping arrangement in the form of several in the circumferential direction successively positioned springs are supported on the cover plates elements or the central disc element and thus allows under Compression of the spring elements the relative rotation of the primary side  with regard to the secondary side, on the one hand by building counter vibrations and on the other hand by generating friction, too Deformation friction in the area of the spring elements themselves, occurring Dampen vibrations.

To prevent the individual spring elements from being relatively strong Torsional vibrations are overloaded, is a rotation angle limitation for the torsional vibration damper arrangement is provided. This includes the turbine shell or an associated ring-like com component on the one hand and on the turbine wheel hub on the other Gearing configurations that interlock with circumferential movement intervention. The torsional vibration damper assembly is approaching one Condition in which the individual spring elements in the maximum permissible Are compressed extent, so the gear arrangements to each other and thus form a non-rotatable bridging of the torsion Vibration damper arrangement and a block protection for the spring elements the same.

The provision of this block protection arrangement by on the turbine wheel shell on the one hand and attached to the turbine wheel hub on the other On the one hand, toothing requires that the generally deformed Sheet metal formed turbine wheel shell connected to a solid component which then has the toothing. On the other hand, it will required, both in this massive component and in the turbine wheel hub to incorporate respective gear configurations, what a additional and complex work process, especially in the area of Turbine wheel hub is.

Based on this state of the art, it is therefore the task of present invention, a hydrodynamic torque converter to provide which, with a simple structure, high operational reliability,  in particular, security against damage to components has the same.

According to the present invention, this object is achieved by a hydrodynamic torque converter comprising a housing, an in the housing with respect to this rotatable about a transducer axis of rotation arranged turbine wheel, which a turbine shell and Has turbine hub, and a torsional vibration damper arrangement tion, wherein a primary side of the torsional vibration damper assembly is connected to the turbine shell and a secondary side of the Torsional vibration damper assembly connected to the turbine hub is, and being the primary and the secondary side against the action a damping arrangement with respect to each other about the transducer axis of rotation are rotatable, one side of the primary side and secondary side two in axially spaced and firmly connected deck disc elements and the other side of the primary side and Secondary side comprises a central disc element which is axially between the two cover plate elements of the primary side is arranged.

In the hydrodynamic torque converter according to the invention further provided that on at least one of the cover plate elements a stop is provided on which the central disc element at Relative rotation between the primary and secondary sides come to rest can.

In contrast to the prior art, the invention Torque converter the function of block protection, d. H. of the overload protection, for the damping arrangement in the torsional vibration damper arrangement itself integrated and is not, as is the case with the prior art the case is integrated into other components of the turbine wheel. This means that with such a torque converter with a so-called turbine damper the structure of both the turbine wheel shell  the turbine hub can be significantly simplified and that nevertheless, a safe block protection for the damping arrangement is provided.

The structure of the hydrodynamic torque wall according to the invention lers can be further simplified in that the two cover plates elements by a plurality of connecting elements with each other are connected and that at least one of the connecting elements Stop forms. In this case, no additional components or Formations on the cover plate element or cover plates elements are provided. The function of the stop is simultaneous also taken over by at least one connecting element that for Connect the two cover plate elements with each other anyway you can see.

To generate the rotation angle limiting function, it is proposed that the central disk element to the at least one of the connections elements assigned has a recess area, which this Interconnected element and in which the connecting element is limited movable in the circumferential direction.

In a preferred embodiment it can be provided that the Cover plate elements through the connecting elements in their radial inner area are connected and that in the central disk element Connecting elements assigned slot-like, in the circumferential direction extending passage recesses are provided.

In the torsional vibration damper according to the invention can also be provided that by at least part of the connecting elements the turbine wheel shell with the primary side of the torsional vibration damper arrangement is connected. In this case, the connecting elements partly take on another function, namely coupling  the turbine shell to the primary side of the torsional vibration damper arrangement. In this way it can be the structure of the invention according to the hydrodynamic torque converter further simplified become.

Alternatively or additionally, it can be provided that the turbine wheel shell preferably in its radially inner area with one of the cover disks elements is connected by a plurality of fasteners. This is particularly the case when using the hydrodynami according to the invention torque converter in connection with commercial vehicles from Advantage, because then the connection stability between the turbine shell and the primary side of the torsional vibration damper assembly further can be increased.

For example, it can be provided that the connecting elements and the Fasteners essentially in the same radial area are arranged and arranged offset to one another in the circumferential direction are. Here it is advantageous for the connecting elements and the fastening Arrange elements alternately in the circumferential direction.

To in a state where the function of torque conversion not the hydrodynamic torque converter according to the invention is required, otherwise in the converter due to the fluid circulation To avoid losses generated, it is proposed that the torque ment converter further has a lock-up clutch through which the turbine wheel optionally for joint rotation with the housing can be coupled. In this case it is further advantageous if one Component in the lock-up clutch on the primary side is non-rotatable is provided. This has the advantage that the torsional vibration damper arrangement of the hydrodynamic torque converter both in Converter operation, i.e. when the lock-up clutch is released, is effective as  even when engaged or at least partially engaged and slip the lock-up clutch is effective.

To connect the component of the lock-up clutch with the Primary side is proposed to be the component of the bridging coupling on at least one of the cover plate elements by a A plurality of attachment elements is attached.

For example, it is possible that the component of the bridging coupling through the attachment elements on one of the cover plates elements is attached. It becomes very stable in this way effective, yet easy to assemble construction achieved.

In the hydrodynamic torque converter according to the invention also be provided that the cover disk elements in their radial outer area by a plurality of connecting elements are connected. It should be noted here that these are radial the outer area of the connecting elements, of course, also the Can take over the function of the aforementioned attack.

In such a configuration, the torsional vibration damper arrangement voltage is then preferably provided that the cover plate elements in its radially outer region connecting elements Form attachment elements.

For example, the lockup clutch component may be a Be inner disk carrier.

In an alternative embodiment, it can be provided that the Turbine wheel shell with the component of the lock-up clutch preferably by welding, most preferably by electrons beam welding or laser welding, is rotatably connected.  

To in addition to that due to the compression of the damping arrangement generated internal friction or deformation losses The occurrence of torsional vibrations increases the frictional effect generate, it is proposed that between the central disc element and at least one of the cover plate elements a friction device works.

Especially when used in commercial vehicles, where also due to the drive units used, relatively high torques are transferred, it is advantageous if the central disc element with the Turbine wheel hub is integrally formed.

Alternatively, however, it is also possible that the central disk element with the turbine wheel hub by welding, preferably electron beam welding or laser welding, is rotatably connected. This shape tion form is particularly advantageous when the turbine hub relatively complex shape is to be provided, so that in the manufacturing process the same does not also apply to the design of the central disc element must be observed.

According to a further aspect of the present invention, a Generic torsional vibration damper can be provided that the Turbine wheel shell in its radially inner area with the primary side of the Torsional vibration damper assembly is connected.

Such a construction has the essential advantage that the turbine wheel shell with the torsional vibration damper arrangement in one area is connected in that they generally have no turbine blades wearing. Access to establishing the connection is thus simplified and there is no need, particularly in the area of the turbine wheel blades Precautions to connect the turbine shell to the torsion Vibration damper arrangement are made.  

It can be provided that the cover disk elements in their radial inner area by a plurality of connecting elements with each other are connected and that the turbine wheel shell by at least one part the connecting elements are connected to the primary side. It is further preferred that the turbine wheel shell with one of the cover plate elements is connected by a plurality of fasteners. It can the arrangement should be such that the connecting elements and the fastening supply elements are arranged in the same radial area and in Are circumferentially offset from each other. Preferably then provided that the fasteners and fasteners elements are arranged alternately in the circumferential direction.

The present invention will hereinafter be described with reference to the accompanying Drawings in detail based on preferred embodiments described. It shows:

Figure 1 is a partial longitudinal sectional view of a torque converter according to the invention.

2 shows a further partial longitudinal section view of the torque transducer of the invention in another segment.

Figure 3 is a partial axial view of a cover discs used in the example shown in Figs 1 and 2, torque converter elements..;

Fig. 4 is a view corresponding to Figure 3, but without Dar position of slot-like recesses in a central disc element.

Fig. 5 is a schematic axial view of a radially inner region of the central disk element inserted in the torque converter according to the invention;

Fig. 6 shows a further partial longitudinal section view of a second Ausgestal tung form of the torque converter according to the invention;

FIG. 7 is a partial longitudinal view of a central disk element used in FIG. 6;

Fig. 8 is a further partial longitudinal sectional view of an alternative embodiment of the torque wall according to the invention;

Fig. 9 is another partial longitudinal sectional view of an alternative embodiment of a torque converter according to the invention;

FIG. 10 is a partial axial view of a central disk element used in the torque converter of FIG. 9;

Fig. 11 shows a modification of the torque converter shown in Fig. 9;

Fig. 12 shows a modification of the embodiment form shown in Figs. 9-11;

Fig. 13 shows a further partial longitudinal sectional view of an embodiment of a hydrodynamic Torque entwandlers invention;

Fig. 14 is a modification of the embodiment shown in Fig. 13;

Fig. 15 shows a further modification of the embodiment shown in Fig. 13.

In Fig. 1, a hydrodynamic torque converter according to the invention 10 is shown. This comprises a housing 12 with a housing cover 14 and an impeller shell 16 of an impeller, generally designated 18 . The impeller shell is fixedly connected to an impeller hub 20 in the radially inner region. The impeller shell 16 also carries a plurality of impeller blades 22 .

A turbine wheel, generally designated 24, is also arranged in the housing 12 . This comprises a turbine wheel shell 26 which carries a plurality of turbine wheel blades 28 in a manner known per se. Furthermore, the turbine wheel 24 comprises a generally designated 30 turbine wheel hub, which is provided for the rotationally fixed connection to an output shaft, whereas the housing cover 14 is provided for the rotationally fixed connection to an input shaft.

A stator 36 with a plurality of stator blades 38 lies axially between the turbine wheel 24 and the pump wheel 18 . The stator 36 is freely rotatable in one direction via a freewheel 38 on a support shaft, not shown.

The turbine wheel shell 26 is connected to the turbine wheel hub 30 via a torsional vibration damper 40, which will be described in more detail below, for common rotation. Furthermore, the torsional vibration damper 40 and thus the turbine wheel 24 can optionally be coupled non-rotatably to the housing 14 via a lock-up clutch generally designated 42. The lock-up clutch 42 comprises a clutch piston 44 which is radially inside and radially outside sealed on the housing cover 14 axially movable and can act on a plurality of clutch plates via a pressure ring 46 . These clutch plates include a pressure plate-like plate 48 , which is acted upon directly by the ring 46 and which is held in a rotationally fixed manner with respect to the housing 12 . For this purpose, a plurality of driving pins 52 extend between the housing cover 14 and a ring 50 connected to it in a rotationally fixed manner. This drive pins 52 engage in the pressure plate-like lamella 48 or enforce in this provided recesses gene. Furthermore, it can be seen that the one or more pins 52 surrounding a helical compression spring 54 is provided, which is on the ring 50 on the one hand and the pressure plate-like lamella 48th on the other hand supports and thus presses it in the direction of a disengaging position of the clutch, so that the clutch piston 44 is also moved via the ring 46 into its disengaged clutch position shown in FIG. 1. A further outer plate 56 is also provided, which is also coupled to the housing 12 by the pins 52 for common rotation.

The lock-up clutch 42 further comprises an inner plate carrier 60 , which has a toothing on its outer circumferential area, with which a plurality of inner plates 64 are in meshing engagement, so that they can be axially displaced with respect to the inner plate carrier 60 in the direction of the converter axis of rotation A. Is conveyed via a fluid line 66 through the output shaft, not shown, fluid into the space formed between the housing cover 14 and the piston 44 , the piston 44 moves to the right and presses the ring 46, the outer plates 48 , 56 against the inner plates 64 , wherein the ring 50 forms an abutment. The inner disk carrier 60 is then uncoupled from the housing 12 for common rotation, wherein depending on the amount of working fluid supplied, slippage can also be made possible.

The torsional vibration damper 40, which can also be seen in FIG. 2, comprises, in a manner known per se, two cover disk elements 70 , 72 which are axially spaced from one another. These cover plate elements are connected in their radially inner area by a plurality of, preferably nine, connecting bolts 74 , with each other, here a spacer sleeve 76 being provided axially between the two cover plate elements 70 , 72 . On the turbine wheel hub 30, a hub disk 78 is performed integrally in the illustrated embodiment, wherein the hub disc 78 is, located axially between the two cover disc elements 70 and 72 radially intervenes between them. In a manner known per se, respective support or control areas, for example in the form of spring windows, are formed in the cover disk elements 70 , 72 and the hub disk 78 , on which the springs 80 of a damping spring arrangement, generally designated 82 , can be supported in the circumferential direction. In this way, against the spring action of the springs 80, the cover disk elements 70 , 72 , which form a primary side 84 of the torsional vibration damper, are rotatable in the circumferential direction about the rotary axis A with respect to the hub disk 78 , which forms a secondary side 86 of the torsional vibration damper 40 . Thus, torsional vibrations occurring in rotary operation can be reduced by building up a counter-vibration or by generating frictional forces.

It can be seen in particular in FIG. 5, which represents a radially inner cutout of the hub disk 78 , that the rivet bolts 74 with the spacer sleeves 76 provided thereon pass through slot-like recesses 88 in the hub disk 78 . Upon relative rotation between the primary side 84 and the secondary side 86 , ie between the cover disk elements 70 , 72 and the hub disk 78 , the connecting bolts 74 with the spacer sleeves 76 provided thereon move in the circumferential direction in each case along the associated slot-like openings or recesses 88 . If a maximum permissible relative rotation angle is reached, the connecting bolts 74 strike the circumferential end regions 90 , 92 of the slot-like recesses 88 and, together with these end regions 90 , 92, form a rotational angle limitation of the torsional vibration damper 40 . In this way, it can be avoided that the springs 80 are placed on the block or are excessively loaded. The springs 80 can thus be formed with a more favorable spring constant, since the excess safety can be minimized. The connecting bolts 74 , which are to be provided anyway in the torsional vibration damper according to the invention, simultaneously provide overload protection or block protection for the damping spring arrangement 82 , so that additional or separate components need not be provided for this.

It can also be seen that in the torsional vibration damper 10 according to the invention the connecting bolts 74 take on a further function, namely the connection of the turbine shell 26 to the torsional vibration damper 40th There are associated with the connecting pin 74, that is provided in the turbine wheel 26 in the radially inner root region corresponding recesses, which bolts of the connection are penetrated 74 so that through the connecting pin 74, the turbine wheel 26 rotatably coupled to the primary side 84th It can be seen that a support disk 94 is additionally provided here, which can be made of hardened material, for example, so that the turbine wheel shell 26 is not damaged when the rivet heads are squeezed together.

Since each of the connecting rivets 74 must be assigned a slot-like recess 88 , the number of connecting rivets 74 is limited in the circumferential direction, since otherwise the torque transmission capacity of the hub disk 78 would be impaired by too many openings. In commercial vehicles, however, it is necessary to create a highly stable connection between the turbine wheel shell 26 and the torsional vibration damper 40 . According to the invention it is therefore additionally provided that in the circumferential direction between each two connecting bolts 74 there is a further connecting bolt 96 through which the turbine wheel shell 26 is riveted only to the cover disk element 72 which is close to it. In addition to, for example, nine connecting rivets 74, a further nine fastening bolts or fastening rivets 96 can thus be provided, so that a total of eighteen riveting points are provided between the torsional vibration damper 40 and the turbine wheel shell 26 . It can be seen in particular in FIG. 2 that the fastening rivets 96 are also supported on the turbine wheel shell 26 with the disk 94 temporarily stored.

The connection of the turbine wheel shell 26 in its radially inner region to the torsional vibration damper 40 also has the following advantage: the connection takes place there in a region in which there are no more turbine wheel blades 28 . That is, the area in which the turbine wheel blades 28 are located is not impaired by the connection of the turbine wheel shell 26 to the torsional vibration damper 40 and can therefore be optimized in terms of flow technology. Furthermore, in particular in the case of commercial vehicles, it is necessary to connect the turbine wheel blades 28 to the turbine wheel shell 26 by soldering. In the construction according to the invention, this process can be carried out before the turbine wheel shell 26 with the turbine wheel blades 28 provided thereon is connected to the torsional vibration damper 40 . In the soldering operation, no impairment of the structural integrity of any components of the torsional vibration damper 40 can thus be introduced.

It can also be seen that in the radially outer region on that deck disc element 70 which is remote from the turbine wheel shell 26 , the inner disk carrier 44 is fixed by a plurality of rivet bolts 98 . It is thus ensured that the torsional vibration damper 40 lies both in the torque transmission path between the lockup clutch 42 and the turbine hub 30 and in the torque transmission path between the turbine shell 26 and the turbine hub 30 and is thus effective as a so-called turbine damper.

It should also be pointed out that in such torque torque converters in converter operation, an axial thrust is generated by the turbine wheel 24 . In order to be able to accommodate these also in the torsional vibration damper 40 , respective support rings 100 , 102 lie between the cover disk elements 70 , 72 and the hub disk 78 , which preferably can also simultaneously take on the function of a friction device. Nevertheless, it is also possible to provide materials with high lubricity with respect to the respective components on which they are supported.

In FIGS. 3 and 4 is a side view of one of the cover discs elements 70, shown 72nd One can see here in particular the spring windows 104 provided in the cover disk elements, against which the springs 80 can be supported in the circumferential direction. It should be pointed out that the support can take place here via respective support elements 106 , so that the material of the cover disk elements 70 , 72 on the one hand and the hub disk 78 on the other hand is relieved. It should also be pointed out that spring sets 104 may be nested in the individual spring windows 104 . In Fig. 3, it also recognizes the circumferential sequence of the connecting bolt or rivet connection 74 and the fixing rivets 96, wherein the connecting pin 74 associated with the individual slot-like recesses 88 are shown. It should be noted that in the torsional vibration damper according to the invention, as shown in FIGS . 1-5, the two cover plate elements 70 , 72 can basically have the same structure, so that the number of parts to be provided is minimized during storage or production can be.

Basically, with regard to the hydrodynamic torque converter shown in FIGS. 1-5, it should also be noted that this is of the 3-line type. That is, a first fluid line leads, as already mentioned, through the output shaft and the channel or the channel arrangement 66 into a space formed between the clutch piston 44 and the housing cover 14 and thus ensures that the clutch piston 44 is brought into the desired axial position becomes. A second line, which is formed, for example, between the impeller hub 20 and the support shaft supporting the stator 36 and leads into the interior of the converter via a space 108 , can be used to supply the working fluid into the interior of the converter, and a third line system, which then between the support shaft and the output shaft is formed, is in communication with an intermediate space 110 , via which, for example, the working fluid can then be removed again from the interior of the converter.

It should also be noted that the type of a lockup clutch shown in connection with the torsional vibration damper 40 according to the invention can be used particularly advantageously. However, another type of lock-up clutch, in particular with a different design or number of the respective clutch plates, could also be provided.

A modification of the torque converter according to the invention is shown in FIGS. 6 and 7. Components which correspond to components described above with regard to structure or function are identified by the same reference number with the addition of appendix "a". In the following, only the constructional differences are essentially dealt with.

It can be seen in the embodiment of the Figs. 6 and 7 that are provided in addition to the provision of the connection rivet or bolt connection 74 a in the radially inner region even in the radially outer region of such connecting bolts or connecting rivets 112 a. By means of this connecting rivet 112 a, the cover disk elements 70 a, 72 a are also firmly connected to one another radially on the outside, and at the same time the inner disk carrier 60 a is connected to the torsional vibration damper 40 a, ie its primary side 84 a. Radially inside the turbine wheel shell 26 a is in turn firmly connected by the connecting rivets 74 a on the one hand and by the fastening rivets 96 a on the other hand to the primary side 84 a of the torsion vibration damper 40 a. Since in this embodiment the cover disk elements 70 a, 72 a and, of course, the hub disk 78 a must first be assembled and the connecting rivets 112 a and 74 a must be inserted, the fastening rivets 96 a must also be used at the same time and can only then be deformed. However, this means that during the deformation process the fastening rivets 96 a axially on the hub disk 78 a, that is, their radially inner region, are supported. Otherwise, the hydrodynamic torque converter 10 a shown in FIGS . 6 and 7 corresponds essentially to the structure and function described above.

A further modification of the hydrodynamic torque converter according to the invention is shown in FIG. 8. Components which correspond to components described above with regard to structure or function are described with the same reference numerals with the addition of an appendix "b".

The structure of the embodiment according to Fig. 8 is such that the turbine wheel 26 b in its radially inner region only via the connecting rivet 74 b to the primary side 84 b of the torsional vibration is connected b spider 40. Although such an embodiment can be considered advantageous from a manufacturing point of view insofar as the previous connection of the cover disk element 72 b to the hub disk 78 b before the entire torsional vibration damper 40 b can be assembled is not required, thus saving one work process and material can. However, due to the smaller number of connection points, such a torsional vibration damper 40 b can only be used to a limited extent in commercial vehicles in which relatively high torques are to be transmitted and is used essentially in motor vehicle torque converters.

A further modification of the torsional vibration damper according to the invention is shown in FIGS . 9-12. Components which correspond in terms of structure and function to components described above are described with the same reference numerals with the addition of an appendix "c". Here, too, the constructional differences are essentially dealt with.

In the embodiment according to FIG. 9 it can be seen that the cover disk elements 70 c, 72 c are only firmly connected to one another in their radially outer region by the connecting rivets or connecting bolts 112 c, here also the inner disk carrier 60 c on the primary side 84 c of the torsional vibration damper is coupled.

Here too, in addition to the inner disk carrier 60 c, a spacer sleeve 120 c can be provided to provide the desired axial distance between the two cover disk elements 70 c, 72 c. The hub disk 78 c extends radially outward into the area of the connecting rivets 112 c and there has slot-like recesses 122 c associated with these connecting rivets 112 c, the function of which essentially corresponds to the function described above with reference to the recesses 88 . That is, the compound c by striking rivets 112 to the peripheral end portions of the recesses is 122 c again a rotational angle limiting for the Dämpfungsfederanord voltage 82 provided c.

It can be seen in Fig. 9, that the radially inner turbine shell back 26 c through the fixing rivets 96 c under temporary storage in said support disk 94 c to the cover disc member 72 is riveted c. The other of the cover disc elements, namely the cover plate member 70 c, and the hub disc 78 c have for this purpose the fixing rivets 96 c associated with respective recesses 126 c, 128 c, through which a tool can then be brought c for pressing the riveted bolt 96th In order not to have to provide such a pair of openings 126 c, 128 c for each of the fastening rivets 96 c, the number of which may be eighteen, for example, it is also possible to provide such an opening 128 in the hub disk 78 c only for every second fastening rivet 96 c c before watch, and then in making the connection, the hub disc 78 c with respect to the cover disc elements 70 c, 72 c to rotate, so that then the openings 128 c in the hub disc 78 c with another set of fastening rivets 96 can be aligned with c.

In Fig. 10 can also be seen in the hub disk 78 c before seen spring window 130 c, on which, as already described above, the springs of the damping arrangement can be supported in the circumferential direction, optionally with intermediate storage of support elements.

A modification of this type of embodiment is shown in FIG . It can be seen here that the hub disk 78 c has radially outer arm or finger sections 132 c, which in turn form recesses between them, in which the respective connecting rivets 112 c can then extend. That is, the material region of the hub disk 78 c, which can be seen in FIG. 10 and extends radially outside the connecting rivets 112 c, is not present. Furthermore, it can be seen that with this type of configuration in the radially inner region, the hub disk 78 c and also the cover disk element 70 c do not have any recesses and openings associated with the fastening rivets 96 c. Rather, in this area lies the pair of sliding or friction rings 100 c, 102 c, a further supporting ring 134 c being located between the friction or sliding ring 102 c and the fastening rivets 96 c. When connecting the radially inner region of the turbine wheel shell 26 c to the cover disk element 72 c, the fastening rivets can then be axially supported on the hub disk 78 c again via the rings 134 c and 102 c during their deformation. If openings 128 c, 126 c are provided, as shown in FIG. 9, then care must be taken that either the rings 100 c, 102 c have corresponding openings or are displaced radially further outwards.

Fig. 12 shows a further modification of the embodiment form described above. It can be seen here in particular that the inner plate carrier 60 c is not designed as a separate component, but is provided integrally with the cover plate element 70 c. In the radially outer area, the inner disk carrier has axially extending projections 140 c, with which corresponding radial projections of the inner disks 64 c mesh. The advantage of this embodiment is that on the one hand no separate component with the primary side 84 c of the torsional vibration damper 40 c has to be connected and that on the other hand the inner lamella lträger 60 c can be produced in a very inexpensive manner by reshaping a sheet metal part and not by introducing a tooth-like configuration into a separately manufactured component. It is pointed out that such a configuration of the inner disk carrier can also be realized in the other illustrated embodiments. It is also fundamentally possible to provide such an inner disk carrier bent from a sheet metal part as a separate component and then to connect it to one of the cover disk elements.

Fig. 13 shows a further alternative embodiment of a torsional vibration damper according to the invention. Components which correspond to the components or components described above with regard to structure or function are identified by the same reference number with the addition of an appendix "d".

The embodiment according to FIG. 13 essentially corresponds to the embodiment described above with reference to FIG. 9. That is, here too, the cover disk elements 70 d, 72 d are connected radially on the outside by the connecting rivets 112 d to one another and at the same time also to the inner disk carrier 60 d. In contrast to the embodiment shown in FIG. 9, however, the turbine shell 26 d is not connected radially inside by riveting to the primary side 84 d of the torsional vibration damper 40 d, but is welded radially outside to an axial end region of the inner disk carrier 60 d. The welding process, which can be done, for example, by laser welding or electron beam welding, makes the riveting process superfluous, but requires great care, since care must be taken to ensure that warping in the region of the turbine wheel 24 d does not occur due to the heat of welding introduced. It can also be seen that in this embodiment the hub disk 78 d is not formed integrally with the turbine wheel hub 30 d. Here, the hub disk 78 d is produced as a separate component and is in turn firmly connected to the turbine wheel hub 30 d by electron beam welding or laser welding. This simplifies in particular the manufacturing process of the turbine hub 30 d, which, as can be seen in the figures, has a relatively complex shape to support the various radial and axial bearing arrangements.

A modification of this embodiment is shown in FIG. 14. In contrast to the embodiment shown in FIG. 13, the hub disk 78 d is here again formed integrally with the turbine wheel hub 30 d and again has the sections or fingers 132 in the radially outer region, as described with reference to the embodiment of FIG. 11 d, between which in the peripheral direction then the Ver bond rivets 112 d are positioned and to which this connection the maximum permissible angle of rotation between the primary side 84 rivets 112 d when reaching d and secondary sides 86 d of the torsional vibration damper 40 can strike d.

A further modification of this type of embodiment is shown in FIG. 15. It can be seen here that the turbine wheel shell 26 d has an axially extending, substantially cylindrical portion 144 d in its radially inner region and is mounted with this on a slide bearing sleeve or sleeve 146 d and is supported radially with respect to the turbine wheel hub 30 d. This embodiment is particularly advantageous since a slight play in the area of the torsional vibration damper 40 d could cause the primary side 84 d to tilt slightly with respect to the secondary side 86 d and thus an uneven support between the turbine wheel shell 26 d and the turbine wheel hub 30 d could be generated. This can be avoided by inserting the sleeve 146 d.

The present invention provides a hydrodynamic torque converter provided, which is a so-called turbine damper acting torsional vibration damper includes. The torsion swin gung damper, whose primary side rotatably with the turbine wheel shell is connected and the secondary side rotatably with the turbine hub is connected, has a rotation angle limitation in order to overload to avoid the damping elements of the same. The angle of rotation limits tongue is taken over by components that are in torsional vibration dampers are present anyway, namely with the respective cover plates connecting bolts or rivets.

Furthermore, the hydrodynamic torque according to the invention converters created the opportunity to combine the turbine wheel shell in one Connect the area with the torsional vibration damper, in which none Turbine wheel blades are located, so that the manufacturing process is simplified can and the turbine wheel shell in the area of the turbine wheel blades can be optimized from a fluidic point of view.

It should be noted that of course the different Aspects of the hydrodynamic torque converter according to the invention, which are recognizable in the various designs, at other configurations can also be used. So is it is of course possible to use the hubs in all configurations disc either as a separate component or as an integral part of the To design the turbine wheel hub. The same applies to the Inner disk carrier, which of course in all design form integral with one of the cover plate elements or as each separate component can be executed.

Claims (23)

1. A hydrodynamic torque converter comprising:

• - a housing ( 12 ; 12 a; 12 b; 12 c; 12 d),
• - A in the housing ( 12 ; 12 a; 12 b; 12 c; 12 d) with respect to this about a converter axis of rotation (A) rotatably arranged turbine wheel ( 24 ; 24 a; 24 b; 24 c; 24 d), which is a turbine wheel shell ( 26 ; 26 a; 26 b; 26 c; 26 d) and a turbine wheel hub ( 30 ; 30 a; 30 b; 30 c; 30 d),
• - A torsional vibration damper arrangement ( 40 ; 40 a; 40 b; 40 c; 40 d), wherein a primary side ( 84 ; 84 a; 84 b; 84 c; 84 d) of the torsional vibration damper arrangement ( 40 ; 40 a; 40 b; 40 c ; 40 d) with the turbine wheel shell ( 26 ; 26 a; 26 b; 26 c; 26 d) is connected and a secondary side ( 86 ; 86 a; 86 b; 86 c; 86 d) of the torsional vibration damper arrangement ( 40 ; 40 a; 40 b; 40 c; 40 d) is connected to the turbine hub ( 30 ; 30 a; 30 b; 30 c; 30 d), and wherein the primary side ( 84 ; 84 a; 84 b; 84 c; 84 d) and the secondary side ( 86 ; 86 a; 86 b; 86 c; 86 d) against the action of a damping arrangement ( 82 ; 82 a; 82 b; 82 c; 82 d) are rotatable with respect to each other about the axis of rotation of the converter (A), one Side from primary side ( 84 ; 84 a; 84 b; 84 c; 84 d) and secondary side ( 86 ; 86 a; 86 b; 86 c; 86 d) two axially spaced and firmly connected cover plate elements ( 70 , 72 ; 70 a, 72 a; 70 b, 72 b; 70 c, 72 c; 70 d, 72 d) and the other side of primary side ( 84 ; 84 a; 84 b; 84 c; 84 d) and the secondary side ( 86 ; 86 a; 86 b; 86 c; 86 d) comprises a central disk element ( 78 ; 78 a; 78 b; 78 c; 78 d) which axially between the two cover disk elements ( 70 , 72 ; 70 a, 72 a; 70 b, 72 b; 70 c, 72 c; 70 d, 72 d) of the primary side ( 84 ; 84 a; 84 b; 84 c; 84 d) is arranged,
  characterized in that on at least one of the cover plate elements ( 70 , 72 ; 70 a, 72 a; 70 b, 72 b; 70 c, 72 c; 70 d, 72 d) a stop ( 74 ; 74 a; 74 b; 112 c; 112 d) is provided, on which the central disc element ( 78 ; 78 a; 78 b; 78 c; 78 d) with relative rotation between the primary side ( 84 ; 84 a; 84 b; 84 c; 84 d) and the secondary side ( 86 ; 86 a; 86 b; 86 c; 86 d).

2. Hydrodynamic torque converter according to claim 1, characterized in that the two cover plate elements ( 70 , 72 ; 70 a, 72 a; 70 b, 72 b; 70 c, 72 c; 70 d, 72 d) by a plurality of connecting elements ( 74 ; 74 a; 74 b; 112 c; 112 d) are connected to each other and that at least one of the connecting elements ( 74 ; 74 a; 74 b; 112 c; 112 d) forms the stop. 3. Hydrodynamic torque converter according to claim 2, characterized in that the central disc element ( 78 ; 78 a; 78 b; 78 c; 78 d) assigned to the at least one of the connecting elements ( 74 ; 74 a; 74 b; 112 c; 112 d) has a recess area ( 88 ; 88 a; 88 b; 122 c; 122 d) through which this connecting element ( 74 ; 74 a; 74 b; 112 c; 112 d) passes and in which the connecting element ( 74 ; 74 a; 74 b; 112 c; 112 d) is limitedly movable in the circumferential direction. 4. Hydrodynamic torque converter according to claim 2 or 3, characterized in that the cover plate elements ( 70 , 72 ; 70 a, 72 a; 70 b, 72 b) by the connecting elements ( 74 ; 74 a; 74 b) in their radially inner region are connected and that in the central disk element ( 78 ; 78 a; 78 b) the connecting elements ( 74 ; 74 a; 74 b) are assigned slot-like, circumferentially extending passage recesses ( 88 ; 88 a; 88 b). 5. Hydrodynamic torque converter according to one of claims 2 to 4, characterized in that by at least part of the connecting elements ( 74 ; 74 a; 74 b), the turbine wheel shell ( 26 ; 26 a; 26 b) with the primary side ( 84 ; 84 a ; 84 b) the torsional vibration damper arrangement ( 40 ; 40 a; 40 b) is connected. 6. Hydrodynamic torque converter according to one of claims 2 to 5, characterized in that the turbine wheel shell ( 26 ; 26 a; 26 c) preferably in its radially inner region with one of the cover disc elements ( 70 , 72 ; 70 a, 72 a; 70 c, 72 c) is connected by a plurality of fastening elements ( 96 ; 96 a; 96 c). 7. Hydrodynamic torque converter according to claim 4 and claim 6, characterized in that the connecting elements ( 74 ; 74 a) and the fastening elements ( 96 ; 96 a) are arranged essentially in the same radial area and are arranged offset in the circumferential direction to one another. 8. Hydrodynamic torque converter according to claim 7, characterized in that the connecting elements ( 74 ; 74 a) and the fastening elements ( 96 ; 96 a) are arranged alternately in the circumferential direction. 9. hydrodynamic torque converter according to one of claims 1 to 8, characterized by a lock-up clutch ( 42 ; 42 a; 42 b; 42 c; 42 d), through which the turbine wheel ( 24 ; 24 a; 24 b; 24 c; 24 d ) can optionally be coupled for common rotation with the housing ( 12 ; 12 a; 12 b; 12 c; 12 d), and in that a component ( 60 ; 60 a; 60 b; 60 c; 60 d) of the lock-up clutch ( 42 ; 42 a; 42 b; 42 c; 42 d) is rotatably provided on the primary side ( 84 ; 84 a; 84 b; 84 c; 84 d). 10. A hydrodynamic torque converter according to claim 9, characterized in that the component ( 60 ; 60 a; 60 b; 60 c; 60 d) of the lock-up clutch ( 42 ; 42 a; 42 b; 42 c; 42 d) on at least one of the Cover plate elements ( 70 , 72 ; 70 a, 72 a; 70 b, 72 b; 70 c, 72 c; 70 d, 72 d) by a plurality of attachment elements ( 98 ; 112 a; 98 b; 112 c; 112 d ) attached or integrally formed with this. 11. A hydrodynamic torque converter according to claim 10, characterized in that the component ( 60 ; 60 b) of the lockup clutch ( 42 ; 42 b) is attached to one of the cover plate elements by the attachment elements ( 98 ; 98 b). 12. Hydrodynamic torque converter according to one of claims 1 to 11, characterized in that the cover plate elements ( 70 a, 72 a; 70 c; 72 c; 70 d; 72 d) in its radially outer region by a plurality of connecting elements ( 112 a ; 112 c; 112 d) are interconnected. 13. Hydrodynamic torque converter according to claim 10 and claim 12, characterized in that the cover plate elements ( 70 a, 72 a; 70 c, 72 c; 70 d, 72 d) in their radially outer region ver connecting elements ( 112 a; 112 c; 112 d) form the attachment elements ( 112 a; 112 c; 112 d). 14. Hydrodynamic torque converter according to one of claims 9 to 13, characterized in that the component ( 60 ; 60 a; 60 b; 60 c; 60 d) of the lock-up clutch an inner plate carrier ( 60 ; 60 a; 60 b; 60 c; 60 d) is. 15. Hydrodynamic torque converter according to one of claims 9 to 14, characterized in that the turbine wheel shell ( 26 d) with the component ( 60 d) of the lock-up clutch ( 42 d) preferably by welding, most preferably by electron beam welding or laser welding, non-rotatably connected is. 16. Hydrodynamic torque converter according to one of claims 1 to 15, characterized in that between the central disc element ( 78 ; 78 a; 78 b; 78 c; 78 d) and at least one of the cover plate elements ( 70 , 72 ; 70 a, 72 a ; 70 b, 72 b; 70 c, 72 c; 70 d, 72 d) a friction device ( 100 , 102 ; 100 a, 102 a; 100 b, 102 b; 100 c, 102 c; 100 d, 102 d) works. 17. Hydrodynamic torque converter according to one of claims 1 to 16, characterized in that the central disc element ( 78 ; 78 a; 78 b; 78 c; 78 d) is integrally formed with the turbine wheel hub. 18. Hydrodynamic torque converter according to one of claims 1 to 16, characterized in that the central disc element ( 78 d) with the turbine wheel hub ( 30 d) by welding, preferably electron beam welding or laser welding, is rotatably connected. 19. Hydrodynamic torque converter according to the preamble of claim 1 or one of claims 1 to 18, characterized in that the turbine wheel shell ( 26 ; 26 a; 26 b; 26 c) in its radially inner region with the primary side ( 84 ; 84 a; 84 b; 84 c) of the torsional vibration damper arrangement ( 40 ; 40 a; 40 b; 40 c) is connected. 20. A hydrodynamic torque converter according to claim 19, characterized in that the cover plate elements ( 70 , 72 ; 70 a, 72 a; 70 b, 72 b; 70 c, 72 c) in their radially inner region by a plurality of connecting elements ( 74 ; 74 a; 74 b; 74 c) are connected to each other and that the turbine wheel shell ( 26 ; 26 a; 26 b; 26 c) is connected to the primary side (at least part of the connecting elements ( 74 ; 74 a; 74 b; 74 c)) 84 ; 84 a; 84 b; 84 c) is connected. 21. A hydrodynamic torque converter according to claim 19 or 20, characterized in that the turbine wheel shell ( 26 ; 26 a; 26 c) with one of the cover plate elements ( 70 , 72 ; 70 a, 72 a; 70 c, 72 c) by a plurality of Fastening elements ( 96 ; 96 a; 96 c) is connected. 22. A hydrodynamic torque converter according to claim 20 and claim 21, characterized in that the connecting elements ( 74 ; 74 a) and the fastening elements ( 96 ; 96 a) are arranged in the same radial area and are offset in the circumferential direction from one another. 23. A hydrodynamic torque converter according to claim 22, characterized in that the connecting elements ( 74 ; 74 a) and the fastening elements ( 96 ; 96 a) are arranged alternately in the circumferential direction.