Abstract:
A device ( 1 ) which is used to modify the control times of an internal combustion engine ( 100 ) is provided. The device ( 1 ) includes a drive wheel ( 13 ), a drive element ( 4 ) and a swashplate mechanism ( 4 ). The torque of the crankshaft ( 101 ) is transferred via a primary drive to the drive wheel ( 13 ) and then, via the swashplate mechanism ( 2 ) to the drive element ( 4 ) which is secured to the camshaft ( 11 ) in a rotationally fixed manner. The configuration of the mounting of the drive wheel ( 13 ) on the tooth support ( 9 ) of the drive element ( 4 ) reduces the axial area of the device ( 1 ) due to the construction measures. The invention also relates to an embodiment, wherein the device ( 1 ) is fixed to the camshaft ( 11 ) by means of a securing screw ( 12   a ) without the need for additional space.

Description:
BACKGROUND 
   The invention relates to a device for modifying the control times of gas-exchange valves of an internal combustion engine according to the preambles of Claims  1  and  6 . 
   In internal combustion engines, camshafts are used for actuating the gas-exchange valves. Camshafts are mounted in the internal combustion engine such that cams mounted on these camshafts contact cam followers, for example, cup tappets, rocker arms, or finger levers. If the camshaft is set in rotation, then the cams roll on the cam followers, which in turn actuate the gas-exchange valves. Thus, both the opening period and also the amplitude, as well as the opening and closing times of the gas-exchange valves, are set by the position and the shape of the cams. 
   Modern engine concepts allow variable valve train designs. On one hand, the valve lift and valve opening period should be made variable up to complete shutdown of individual cylinders. For this purpose, concepts such as switchable cam followers, variable valve trains, or electrohydraulic or electrical valve actuators are provided. Furthermore, it has been shown to be advantageous to be able to influence the opening and closing times of the gas-exchange valves during the operation of the internal combustion engine. It is likewise desirable to be able to influence the opening or closing times of the inlet or outlet valves separately, in order, for example, to be able to selectively set a defined valve overlap. By setting the opening or closing times of the gas-exchange valves depending on the current engine-map range, for example, the current rotational speed or the current load, the specific fuel consumption can be lowered, which has a positive effect on the exhaust-gas behavior and increases the engine efficiency, the maximum torque, and the maximum output. 
   The described variability in the gas-exchange valve time control is implemented through a relative change of the phase position of the camshaft relative to the crankshaft. Here, the camshaft is usually in a driven connection with the crankshaft via a chain drive, belt drive, gearwheel drive, or equivalent drive concepts. Between the chain drive, belt drive, or gearwheel drive driven by the crankshaft and the camshaft there is a camshaft adjuster, which transmits the torque from the crankshaft to the camshaft. Here, this device for modifying the control times of the internal combustion engine is constructed such that during the operation of the internal combustion engine, the phase position between the crankshaft and camshaft is held reliably and, if desired, the camshaft can be rotated within a certain angular range relative to the crankshaft. 
   In internal combustion engines with separate camshafts for the intake and exhaust valves, these can each be equipped with a camshaft adjuster. Therefore, the opening and closing times of the intake and exhaust gas-exchange valves can be shifted in time relative to each other and the valve overlaps are set selectively. 
   The seat of modern camshaft adjusters is generally located on the drive-side end of the camshaft. It is comprised of a crankshaft-fixed drive wheel, a camshaft-fixed driven element, and an adjustment mechanism transmitting the torque from the drive wheel to the driven part. The drive wheel can be constructed as a chain, belt, or gearwheel and is locked in rotation with the crankshaft by means of a chain, belt, or gearwheel drive. The adjustment mechanism can be operated electromagnetically, hydraulically, or pneumatically. Mounting the camshaft adjuster on an intermediate shaft or supporting it on a non-rotating component is similarly conceivable. In this case, the torque is transmitted via additional drives to the camshaft. 
   Electrically operated camshaft adjusters are comprised of a drive wheel, which is in driven connection with the crankshaft of the internal combustion engine, a driven part, which is in driving connection with a camshaft of the internal combustion engine, and adjustment gearing. The adjustment gearing involves a triple-shaft gear mechanism, with three components rotating relative to each other. Here, the first component of the gearing is locked in rotation with the drive wheel and the second component is locked in rotation with the driven part. The third component is constructed, for example, as a toothed component, whose rotational speed can be regulated via a shaft, for example, by means of an electric motor or a braking device. 
   The torque is transmitted from the crankshaft to the first component and from there to the second component and thus to the camshaft. This happens either directly or under intermediate connection of the third component. 
   Through suitable regulation of the rotational speed of the third component, the first component can be rotated opposite the second component and thus the phase position between the camshaft and crankshaft can be changed. Examples for such triple-shaft gear mechanisms are internal eccentric gear mechanisms, double-internal eccentric gear mechanisms, shaft gear mechanisms, swashplate gear mechanisms, or the like. 
   For controlling the camshaft adjuster, sensors detect the characteristic data of the internal combustion engine, for example, the load state, the rotational speed, and the angular positions of the camshaft and crankshaft. This data is fed to an electronic control unit, which controls the adjustment motor of the camshaft adjuster after comparing the data with an engine-map range of the internal combustion engine. 
   From DE 102 22 475 a device for modifying the control times of an internal combustion engine is known, in which the torque transfer from the crankshaft to the camshaft and the adjustment process are realized by means of a swashplate gear mechanism. The device essentially comprises a camshaft-fixed driven element and a swashplate. The device further has a drive wheel, which is in driven connection with a crankshaft and is constructed in one piece with a housing. The swashplate is provided with four pins engaging in elongated holes of the housing. The torque of the crankshaft is transmitted via the drive wheel, the housing, and the pins to the swashplate. 
   The device further has an adjustment shaft, which is driven, for example, by an electric motor and on which the swashplate is supported at a defined contact angle. 
   The swashplate is provided on its axial side surface facing the driven element with conical gearwheel teeth and arranged at a certain contact angle to the driven element, such that an angle segment of the teeth of the swashplate engages in an angle segment of conical gearwheel teeth constructed on the driven element. Here, there is a difference in the number of teeth in the conical gearwheels. 
   A rotation of the adjustment shaft relative to the driven element leads to a wobbling rotation of the swashplate and thus to a rotation of the engaged angle segment relative to the driven element. Due to the difference in the number of teeth of the conical gearwheels, this leads to relative rotation of the camshaft relative to the crankshaft. 
   The drive wheel or the housing is supported on an axial shoulder of the driven element so that it can rotate relative to this element. The conical gearwheel teeth of the driven element are constructed on a teeth carrier, wherein the teeth carrier is mounted before the shoulder in the axial direction. The teeth carrier and a cover screwed to the drive wheel form an axial bearing for the drive wheel or the housing. Here, the cover is fixed in the axial direction by the driven element on one side and by the camshaft on the other side. 
   The construction of a bearing shoulder on the driven element and the teeth carrier arranged offset axially to this element lead to a relatively large need for axial installation space for the device and to a complex geometrical shape for the driven element. 
   Furthermore, the driven element is locked in rotation with the camshaft by means of an attachment screw. The screw head engages from the side facing away from the camshaft through the device, wherein its threads engages in complementary internal threads constructed in the camshaft. The screw head exerts a force on the driven element, whereby this is fixed to the camshaft. 
   The screw head is used simultaneously as the race for the cylinder bodies of a needle bearing, by means of which the adjustment shaft is supported on the screw head. In order to be able to be used as the race for the needle bearing, the screw head must be subjected to a hardening process, wherein care must be taken that the threaded section is not hardened. Such hardening processes are complicated and expensive. Simultaneously, the solid screw head leads to a high mass and thus to a high inertia of the arrangement. 
   SUMMARY 
   The invention is based on the objective of creating a device for modifying the control times of gas-exchange valves of an internal combustion engine, wherein the axial installation space requirements and the mass of the device are reduced and the production costs are to be reduced. 
   In a first embodiment of a device for modifying the control times of gas-exchange valves of an internal combustion engine with a drive wheel in driven connection with a crankshaft and with a swashplate gear mechanism, which has a housing and a driven element in driving connection with a camshaft, wherein a radially outer ring section of the driven element is constructed as a teeth carrier, wherein a toothed carrier is constructed on an axial side surface of the teeth carrier and wherein the drive wheel or the housing is supported on the drive element so that it can rotate relative to the drive element. According to the invention, the objective is met in that an outer casing surface of the teeth carrier is used as a radial bearing surface for the housing or the drive wheel. 
   In the embodiment according to the invention, the device is comprised of a drive wheel constructed as a belt, chain, or gearwheel and a swashplate gear mechanism. Among other things, the swashplate gear mechanism comprises a housing, which is locked in rotation with the drive wheel, a swashplate, a driven element, which is locked in rotation with a camshaft, and an adjustment shaft, which is driven, for example, by means of an electric motor. The housing can be constructed in one piece with the drive wheel or can be connected with this with a firmly bonded, positive, or form fit. Torque is transmitted from the crankshaft to the drive wheel and thus to the housing via a belt, chain, or gearwheel drive. The housing is actively connected by means of a pin coupling or a toothed component with the swashplate. As a toothed component, for example, a conical gearwheel is conceivable, which is constructed in one piece with the housing or is connected to the housing by means of attachment means. The pin coupling or the toothed component transmits the torque transmitted by the crankshaft to the drive wheel to the swashplate, which is supported on an adjustment shaft. The swashplate is arranged on an adjustment shaft at a defined contact angle relative to the driven element. 
   A toothed ring running in the peripheral direction is constructed on an axial side surface of the swashplate. Furthermore, a ring-shaped, radially outer area of the driven element is constructed as a teeth carrier, on which a toothed ring is also formed. The toothed ring of the swashplate engages along a peripheral-side angle segment in the toothed ring of the driven element. 
   The crankshaft torque is transmitted via the drive wheel, the housing, the pin coupling, or the toothed component to the swashplate and from there to the driven element and finally to the camshaft. The toothed rings of the swashplate and the driven element or the swashplate and the toothed component, or both gear pairs, have different numbers of teeth. If the adjustment shaft rotates at the rotational speed of the drive wheel, then the phase position between the crankshaft and the camshaft is maintained. If there is a difference between the rotational speed of the adjustment shaft and the rotational speed of the drive wheel, then the phase position between the camshaft and the crankshaft is changed. Here, the housing and the drive wheel rotate relative to the driven element, which supports the housing or the driven wheel in the radial direction. 
   By supporting the drive wheel or the housing on the outer casing surface of the teeth carrier, the necessity of providing the driven element with an axial shoulder is eliminated, whereby the axial installation space of the swashplate gear mechanism can be reduced considerably. 
   In one actual implementation of the invention, the toothed ring transitions in the radial direction outwardly into a ring-shaped bearing section, which has a closed outer casing surface. 
   In this embodiment, a ring-shaped edge connects to the toothed ring at the outside in the radial direction, which is used as a radial bearing surface for the drive wheel or the housing. The edge forms in the peripheral direction a closed bearing surface without interruption, which aids the construction of a hydrodynamic lubricating film. 
   The production of the teeth of the toothed ring is possible, for example, by means of wobble pressing, axial rolling, milling, or sintering. 
   Alternatively, it can be provided that the teeth of the toothed ring extend in the radial direction up to the radial bearing surface. The teeth intersect the bearing surface in this case. Through correspondingly rounded edge geometries, the necessary bearing capacity and wear resistance can be achieved. This embodiment has the advantage of lower production costs. 
   In one advantageous improvement of the invention, it is provided that the axial surface of the teeth carrier facing away from the toothed ring in the axial direction forms a first axial bearing surface for axial bearing of the housing or the drive wheel. 
   In this embodiment, the driven element or the housing is constructed with a projection, which extends radially inwards and which contacts the axial side surface of the driven element facing away from the toothed ring in the area of the teeth carrier. The projection advantageously involves a ring-shaped element, which extends on an axial side surface of the drive wheel or the housing. Thus it is guaranteed that axial forces acting on the drive wheel or the housing and directed away from the camshaft are received by the driven element. The projection can be constructed in one piece with the driven wheel or the housing or produced separately and fixed to the drive wheel or to the housing. The projection is advantageously constructed with a ring shape extending around the entire device. In this case, additional functions can be integrated into the ring-shaped projection, for example, a rotational angle limiter of the drive wheel relative to the driven element. For this purpose, the ring-shaped projection can be constructed with an additional projection, which engages in a connecting rod in the driven element. Alternatively, the ring-shaped projection can be provided on its radially inner end with a recess, in which a projection constructed or fixed on the driven element engages. 
   In the case of small rotating moments about the radial bearing position of the housing or the driven wheel, axial forces to be directed to the camshaft can be supported by means of the gear pair between the swashplate and the toothed component. 
   Furthermore, it can be provided that the toothed ring-side axial side surface of the ring-shaped bearing section forms a second axial bearing surface for axial bearing of the housing or the drive wheel. 
   In this case, an additional projection extending radially inwards is provided on the housing or on the drive wheel, which is supported in the axial direction on the ring-shaped edge of the teeth carrier. 
   In this way, it is possible, similar to the embodiment in the state of the art, to construct both the radial and also the axial bearing positions on the components of the driven element and drive wheel or housing, possibly including a stop plate, wherein the axial installation space requirements are reduced considerably. 
   In a second embodiment of a device for modifying the control times of gas-exchange valves of an internal combustion engine with a swashplate gear mechanism, wherein the swashplate gear mechanism comprises at least one swashplate, which is supported on an adjustment shaft, the objective of the invention is met in that the adjustment shaft is supported on a hollow shaft, wherein the hollow shaft is locked in rotation with the camshaft by means of an attachment screw and a radially inwardly extending collar, on which a screw head of the attachment screw is supported, is constructed on an inner casing surface of the hollow shaft. 
   In an advantageous refinement of the invention, it is provided that the collar is arranged such that the screw head, in the assembled state of the device, is arranged on the camshaft completely within the hollow shaft. 
   The adjustment shaft is supported in this embodiment on a hollow shaft, preferably by means of a rolling bearing. An outer casing surface of the hollow shaft is used as an inner running surface for the cylinder bodies of the rolling bearing. Furthermore, the hollow shaft is connected to the camshaft by means of an attachment screw, wherein the driven element is included in the clamping connection and is likewise fixed to the camshaft. Here, the screw head of the attachment screw is supported on a collar constructed in the interior of the hollow shaft. By supporting the adjustment shaft on a hollow shaft, the weight of the device is reduced considerably. The hollow shaft can be further produced cost effectively in a non-cutting shaping process, for example, as a sintered or molded sheet part. This reduces the costs of the device in comparison with the embodiment from the state of the art, because expensive special screws can be eliminated. 
   In this embodiment, the collar is constructed so that the forces, which are exerted by the attachment screw on the hollow shaft and which are produced due to the tightening moment in the assembly of the device on the camshaft, are led at least to a great degree to the rolling bearings, which support the adjustment shaft relative to the hollow shaft. For this purpose it is necessary to arrange the collar as close as possible to the device-side end of the camshaft within the hollow shaft. This has the consequence that the screw head of the attachment screw, which transmits the clamping force to the hollow shaft, is arranged completely within the hollow shaft and thus contributes nothing to the installation length of the device. 
   Another advantage of this embodiment relative to an embodiment, in which the screw head attaches to the end of the hollow shaft facing away from the camshaft, lies in that expansion of the hollow shaft is prevented. If the screw head contacts the end of the hollow shaft away from the camshaft, then this lies within the clamping connection of the attachment screw on its entire axial length. This has the consequence that the hollow shaft is flattened and bulges. The bulging of the hollow shaft leads to a reduction in the bearing play of the rolling bearing arranged on it or to seizing of the slide bearing, whereby higher friction occurs in the device and in the worst case it becomes non-functional. 
   Furthermore, the clamping force generates high tensions in the hollow shaft, whereby plastic deformations occur in this event. Due to the undesired plastic deformations, automated mounting of the device on the camshaft becomes more difficult, because a defined end of the mounting process cannot be detected by the mounting device due to the setting force losses. 
   These disadvantages do not occur or only occur to a much lower extent in the embodiment according to the invention. 
   Furthermore, the attachment screw can be shorter and thus lighter, whereby the mass and the inertia of the device is further reduced. 

   
     BRIEF DESCRIPTION OF THE DRAWINGS 
     Additional features of the invention emerge from the following description and the associated drawings, in which embodiments of the invention are shown schematically. Shown are: 
       FIG. 1   a  a view of an internal combustion engine, only very schematically, 
       FIG. 1  a longitudinal cross-sectional view through a first embodiment according to the invention of a device for modifying the control times of gas-exchange valves of an internal combustion engine, 
       FIG. 2  a longitudinal cross-sectional view through a second embodiment according to the invention for a device for modifying the control times of gas-exchange valves of an internal combustion engine, 
       FIG. 3  a longitudinal cross-sectional view through a third embodiment according to the invention for a device for modifying the control times of gas-exchange valves of an internal combustion engine, 
       FIG. 4  a longitudinal cross-sectional view through a fourth embodiment according to the invention for a device for modifying the control times of gas-exchange valves of an internal combustion engines, 
       FIG. 5 , a longitudinal cross-sectional view through a fifth embodiment according to the invention for a device for modifying the control times of gas-exchange valves of an internal combustion engine. 
   

   DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
   In  FIG. 1   a , a schematic of an internal combustion engine  100  is shown, wherein a piston  102  sitting on a crankshaft  101  is shown in a cylinder  103 . The crankshaft  101  is connected in the shown embodiment via a power-transmission means drive  104  and  105  to an intake camshaft  106  and exhaust camshaft  107 , respectively, wherein first and second devices  1  can provide for a relative rotation between the crankshaft  101  and camshafts  106 ,  107 . Cams  108 ,  109  of the camshafts  106 ,  107  actuate an intake gas-exchange valve  110  and the exhaust gas-exchange valve  111 , respectively. 
     FIG. 1  shows an embodiment of a device  1  according to the invention for modifying the control times of an internal combustion engine  100 . The device  1  comprises, among other things, a swashplate gear mechanism  2  comprised of a toothed component  3   a , a driven element  4 , and a swashplate  5 . The toothed component  3   a  is constructed in the shown embodiment as a conical gearwheel  3 . A first toothed ring  6  constructed as conical gearwheel teeth is formed on an axial side surface of the conical gearwheel  3 . Furthermore, on the axial side surfaces of the swashplate  5  there is a second and a third toothed ring  7 ,  8 , wherein the toothed rings  7 ,  8  in this embodiment are each constructed similarly as conical gearwheel teeth. Here, the second toothed ring  7  is constructed on the axial side surface facing the conical gearwheel  3  and that of the toothed ring  8  is constructed on the axial side surface of the swashplate  5  facing the driven element  4 . The radial outer section of the driven element  4  is constructed as toothed carrier  9 , on whose axial side surface facing the swashplate  5  there is a fourth toothed ring  10 . The fourth toothed carrier  10  is constructed in this embodiment likewise as conical gearwheel teeth. 
   The driven element  4  is locked in rotation with a camshaft  11 . The connection between the driven element  4  and camshaft  11  is realized in the shown embodiment by means of a first attachment means  12 , here an attachment screw  12   a . Firmly bonded, positive, friction, or form fit connection methods are also conceivable. 
   A drive wheel  13  is in active connection with a not-shown primary drive, by means of which a torque is transmitted from the crankshaft  101  to the drive wheel  13 . Such a primary drive can be, for example, a chain, belt, or gearwheel drive. The drive wheel  13  is locked in rotation with a housing  14 , and the housing  14  is in turn locked in rotation with the conical gearwheel  3 . In the embodiment shown in  FIG. 1 , these are constructed in one piece. Alternatively, the housing  14  can be connected to the conical gearwheel  3  and/or to the drive wheel  13  with a firmly bonded, positive, friction, or form fit. 
   The conical gearwheel  3  and the driven element  4  are parallel to each other and are spaced apart in the axial direction. Together with the housing  14 , the conical gearwheel  3  and the driven element  4  form a ring-shaped hollow space, in which the swashplate  5  is arranged. By means of first rolling bearings  15 , the swashplate  5  is supported at a defined contact angle to the conical gearwheel  3  and the driven element  4  on an adjustment shaft  16 . The essentially pot-shaped adjustment shaft  16  is provided with a coupling element  17 , in which a not-shown shaft of a similarly not-shown device engages, with which the rotational speed of the adjustment shaft  16  can be regulated. The adjustment shaft  16  is supported by means of a second rolling bearing  18  on a shaft  19   a  locked in rotation with the camshaft  11  and constructed in the present embodiment as a hollow shaft  19 . 
   The swashplate  5  arranged at a defined contact angle on the adjustment shaft  16  engages with the second toothed ring  7  in the first toothed ring  6  of the conical gearwheel  3  and with the third toothed ring  8  in the fourth toothed ring  10  of the driven element  4 . Here, the toothed rings  6 ,  7 ,  8 ,  10  engage only at a certain angular range, wherein the size of the angular range is dependent on the contact angle of the swashplate  5 . 
   By means of the engagement of the toothed rings  6 ,  7 ,  8 ,  10 , the torque of the crankshaft  101  transmitted by the primary drive to the drive wheel  13  and from there to the conical gearwheel  3  is transmitted via the swashplate  5  to the driven element  4  and thus to the camshaft  11 . 
   In order to maintain the phase position between the camshaft  11  and crankshaft  101 , the adjustment shaft  16  is driven at the rotational speed of the drive wheel  13 . If the phase position is changed, then the rotational speed of the adjustment shaft  16  increases or decreases depending on whether the camshaft  11  advances or lags relative to the crankshaft  101 . Through the different rotational speed of the adjustment shaft  16 , the swashplate  5  executes a wobbling rotation, wherein the angular ranges, in which the toothed rings  6 ,  7 ,  8 ,  10  engage each other, run around the swashplate  5 , the conical gearwheel  3 , and the driven element  4 . In at least one of the toothed ring pairs  6 ,  7 ,  8 ,  10 , the two intermeshing toothed rings  6 ,  7 ,  8 ,  10  have different numbers of teeth. If the angular ranges, in which the toothed rings  6 ,  7 ,  8 ,  10  intermesh, have completed one run, then an adjustment of the conical gearwheel  3  relative to the driven element  4  and thus the camshaft  11  relative to the crankshaft  101  is produced due to the difference in the number of teeth. The adjustment angle corresponds to the area that the teeth forming the difference in the number of teeth enclose. 
   In this connection, it is conceivable that the toothed rings  6 ,  7 ,  8 ,  10  of both toothed ring pairs have different numbers of teeth. Thus, the adjustment conversion ratio is given from the two resulting difference ratios. 
   It is likewise conceivable that the toothed rings  6 ,  7 ,  8 ,  10  have only one toothed ring pair with different numbers of teeth. The conversion ratio in this case is given only based on this speed reduction. The other toothed ring pair is used in this case only as coupling means with a speed-reduction ratio of 1:1 between the swashplate  5  and the corresponding component  3 ,  4 . 
   During the adjustment process, the drive wheel  13  or the housing  14  rotates according to the conversion ratio and the rotational speed of the adjustment shaft  16  to the driven element  4 . The drive wheel  13  or the housing  14  is supported on an outer casing surface  20  of the teeth carrier  9 . Therefore, the formation of an axial shoulder on the driven element  4 , as provided in DE 102 22 475 A1, is eliminated. This leads to a lower axial installation length of the swashplate gear mechanism  2  and thus the device  1 . 
   In the embodiment shown in  FIG. 1 , the teeth of the fourth toothed ring  10  extend along the entire length of the teeth carrier  9  and thus partially interrupt the outer casing surface  20  of the teeth carrier  9  formed as radial bearing surface  23   a . Also conceivable is to allow the teeth of the fourth toothed ring  10  to transition in the radial direction outwards into a ring-shaped bearing section  23 , whereby the outer casing surface  20  of the teeth carrier  9  is formed as an uninterrupted radial bearing surface  23   a.    
   Furthermore, in the shown embodiment there is a stop plate  21 , which is connected with a positive, friction, firmly bonded, or form fit with the drive wheel  13  or the housing  14 . Also conceivable is an attachment of the stop plate  21  with one of the two components  13 ,  14  by means of a screw connection. 
   The stop plate  21  extends in the radial direction farther inwards than the drive wheel  13  or the housing  14  and is arranged such that an axial side surface of the stop plate  21  contacts the axial side surface of the driven element  4  facing away from the fourth toothed ring  10  in the area of the teeth carrier  9 . Thus, the stop plate  21  interacting with the teeth carrier  9  forms an axial bearing for the drive wheel  13  and the housing  14 , which receives axial forces acting on these components  13 ,  14  in the direction away from the camshaft  11 . 
   If smaller tilting moments act on the drive wheel  13 , then axial forces acting on the drive wheel  13  in the direction of the camshaft  11 , as shown in  FIG. 1 , are supported on the conical gearwheel  3  and the swashplate  5  by means of the engaged toothed rings  6 ,  7 . Thus, both the radial and also axial support of the drive wheel  13  and the housing  14  is guaranteed, wherein the axial installation space requirements of the swashplate gear mechanism  2  are reduced considerably. 
     FIG. 2  shows another embodiment according to the invention for a device  1 . The devices  1  shown in  FIGS. 1 and 2  are essentially identical. In contrast with the embodiment shown in  FIG. 1 , in the embodiment shown in  FIG. 2  the drive wheel  13  and the housing  14  are not constructed in one piece. Instead these involve separate components, which are connected to each other with a positive, firmly bonded, friction, or form fit. Also conceivable would be a connection of the two components by means of a screw connection. The drive wheel  13  is provided with elongated holes  22  oriented on the peripheral side, in order to reduce the mass and thus the inertia of the device  1 . 
   As in the first embodiment, here the housing  14  and thus the drive wheel  13  are supported on the teeth carrier  9  of the driven element  4 . In contrast with the first embodiment, the teeth of the fourth toothed ring  10  do not extend up to the radial bearing surface  23   a , but instead transition into a ring-shaped bearing section  23 . Therefore, a closed radial bearing surface  23   a  is created, on which the housing  14  is rotatably supported. 
   As in the first embodiment, a stop plate  21 , which acts with the driven element  4  as an axial stop for the housing  14 , is mounted on the housing  14 . Axial forces acting on the drive wheel  13  in the direction of the camshaft  11  are in turn supported on the conical gearwheel  3  and the swashplate  5 , in turn, by means of the two toothed rings  6 ,  7 . 
     FIG. 3  shows a third embodiment according to the invention for the device  1 , wherein in this embodiment the drive wheel  13  is constructed in one piece with the stop plate  21 . The drive wheel  13  is in turn supported radially on the outer casing surface  20  of the teeth carrier  9 . The axial support is in this case guaranteed on one side by the interaction of the stop plate  21  and an axial side surface of the driven element  4  and on the other side by means of the housing  14  and the toothed ring-side axial side surface of the teeth carrier  9  of the driven element  4 . The drive wheel  13  and the housing  14  are locked in rotation with each other in this embodiment, wherein positive, firmly bonded, friction, or form fit connections can be used. Also conceivable would be a screw connection of both components. 
   Through the construction of an additional axial bearing position between the housing  14  and the teeth carrier  9  of the driven element  4 , axially directed forces, which act in the direction of the camshaft  11  on the drive wheel  13 , are no longer supported on the toothed rings  6 ,  7  of the conical gearwheel  3  and the swashplate  5 . Therefore, larger tilting moments acting on the drive wheel  13  can also be supported with a reliable function without also loading the toothed rings  6 ,  7 . Therefore, the teeth lash of the toothed rings  6 ,  7  is not negatively affected, which leads to improved efficiency, and seizing of the device  1  can be avoided. 
   Similar concepts as in the third embodiment are shown in  FIGS. 4 and 5 . In  FIG. 4 , the housing  14  is formed in one piece with the drive wheel  13 , while the conical gearwheel  3  and the stop plate  21  are produced separately. The three components are connected to each other by means of second attachment means  24 . In the shown embodiment, this involves a screw connection. The housing  14  is in turn supported radially on an outer casing surface  20  of the teeth carrier  9  of the driven element  4 . As an axial bearing, the stop plate  21 , which interacts with an axial side surface of the driven element  4 , is used in turn on one side. On the other side of the driven element  4 , this interacts in the area of the teeth carrier  9  with a radially inwards extending projection  25  of the housing  14 . 
   The embodiment in  FIG. 5  is essentially identical to that in  FIG. 4 , with the exception that the drive wheel  13  is formed in one piece with the stop plate  21  and the housing  14  is shown as a separate component. 
   The radial projections  25  of the embodiments shown in  FIGS. 4 and 5  have a ring shape, whereby the housing  14  is supported axially by means of a ring-shaped surface relative to the driven element  4 . Conceivable in connection with this are also projections  25 , which are formed only in defined angle segments of the housing  14 , which leads to a reduction in mass of the device  1 . 
     FIGS. 1 to 5  show another aspect of the invention. In the shown embodiments, the swashplate  5  is supported by means of second rolling bearing  18  on a hollow shaft  19 . The hollow shaft  19  and the driven element  4  are locked in rotation on the camshaft  11  by means of an attachment screw  12   a . The attachment screw  12   a  engages with its threaded section in a hollow space  26  provided with internal threads in the camshaft  11 . A screw head  27  contacts a collar  28  formed on the inner casing surface of the hollow shaft  19  and charges this with a clamping force directed towards the camshaft  11 . The hollow shaft  19  forwards the clamping force to the driven element  4 , which is supported on the camshaft  11 . For this purpose, the hollow shaft  19  is provided in the shown embodiments with a step  29 , so that the driven element  4  is pressed by the step  29  onto the camshaft  11 . 
   The collar  28  is advantageously formed in the axial direction in the direct surroundings of the step  29 . Here, embodiments are imaginable, in which the collar  28  is formed in the axial direction between the step  29  and the camshaft  11  or, as shown in the figures, on the side of the step  29  facing away from the camshaft. 
   Through the construction of the collar  28  within the hollow shaft  19  in the area of the step  29 , the entire screw head  27  is located within the hollow shaft  19 , whereby this does not increase the axial installation length of the device  1 . In comparison with an embodiment, in which the screw head  27  contacts the side of the hollow shaft facing away from the camshaft, in this embodiment, stresses are largely prevented in the material of the hollow shaft  19 , which could lead to its expansion. This is especially important for the area of the races of the cylinder bodies. Therefore, it is guaranteed that the operating play of the second rolling bearing  18  is not reduced. Furthermore, the degree of plastic deformation of the hollow shaft  19  is decreased, whereby automated mounting is allowed. 
   The use of a hollow shaft  19  as an inner raceway for the cylinder bodies of the second rolling bearing  18  leads to a significant reduction of the rotating masses in comparison with the embodiment in the state of the art. Furthermore, expensive special screws can be eliminated, whose screw heads are used as raceways. Such screws would have to be subjected to complicated and expensive hardening processes, wherein hardening of the threaded section would have to be avoided. In contrast, the hollow shaft can be formed as an economical and easy to produce molded sheet part. Alternatively, sintered components or the like are also conceivable. 
   In  FIGS. 1 to 5 , a stop plate  21  is provided on the end of the device  1  facing the camshaft. In  FIGS. 1 ,  2 , and  4 , this is constructed as a separate component, which is fixed to the drive wheel  13  or the housing  14  with a positive, firmly bonded, friction, or form fit or by means of a screw connection. In  FIGS. 3 and 5 , this is constructed in one piece with the drive wheel  13 . The stop plate  21  forms a part of a rotational angle limiter in the shown embodiments. Here, the radially inner, ring-shaped casing surface of the stop plate  21  is provided with at least one recess  30  running in the peripheral direction, in which a tab  31  formed on the driven element  4  engages. The recess  30  extends in the peripheral direction over an angle segment, which corresponds to the maximum permissible adjustment angle plus the angle extent of the tab  31 . The tab  31  can be constructed in one piece with the driven element  4  or can be comprised of a separate component, which is fixed on the driven part  4 . Also conceivable is forming the tabs  31  on the stop plate  21  and the recess  30  on the driven element  4 . Also conceivable is providing several recesses  30 , in each of which one tab  31  engages. 
   If the phase position of the camshaft  11  relative to the crankshaft  101  changes, the relative position of the tab  31  in the recess  30  also changes. In the extreme case, the tab  31  comes into contact with a radial wall of the recess  30 , whereby further adjustment of the phase position is effectively prevented in this direction. 
   LIST OF REFERENCE NUMBERS 
   
       
         1  Device 
         2  Swashplate gear mechanism 
         3  Conical gearwheel 
         3   a  Component 
         4  Driven element 
         5  Swashplate 
         6  First toothed ring 
         7  Second toothed ring 
         8  Third toothed ring 
         9  Teeth carrier 
         10  Fourth toothed ring 
         11  Camshaft 
         12  First attachment means 
         12   a  Attachment screw 
         13  Drive wheel 
         14  Housing 
         15  First rolling bearing 
         16  Adjustment shaft 
         17  Coupling element 
         18  Second rolling bearing 
         19  Hollow shaft 
         19   a  Shaft 
         20  Outer casing surface 
         21  Stop plate 
         22  Elongated holes 
         23  Bearing section 
         23   a  Radial bearing surface 
         24  Second attachment means 
         25  Projection 
         26  Hollow space 
         27  Screw head 
         28  Collar 
         29  Step 
         30  Recess 
         31  Tab 
         100  Internal combustion engine 
         101  Crankshaft 
         102  Piston 
         103  Cylinder 
         104  Power-transmission means drive 
         105  Power-transmission means drive 
         106  Intake camshaft 
         107  Exhaust camshaft 
         108  Cam 
         109  Cam 
         110  Inlet gas-exchange valve 
         111  Outlet gas-exchange valve