in the camshaft drive 10 according to the invention , a camshaft adjuster 13 is used for adjusting the angular position between a drive element 11 driven by a traction mechanism , for example , by a chain or a belt , and a camshaft 12 according to a control device , which determines a suitable control signal for adjusting the camshaft adjuster 13 , in particular , under consideration of power output demands of the driver , emission requirements , fuel - conservation requirements , and engine , operating , and environmental parameters . in the camshaft drive 10 , any camshaft adjuster can be used , which works on the basis of a superposition gear mechanism or a triple - shaft gear mechanism . in such a gear mechanism , the transmission ratio of the drive movement of the drive element 11 to the camshaft 12 depends on the movement of the adjustment shaft 14 , which is drivingly connected to a control drive . in the embodiment shown in fig1 , the gear mechanism involves a double - eccentric gear mechanism . in this embodiment , the adjustment shaft 14 enters into a central bore of a double - eccentric shaft 15 through a drive connection , or optionally through an elastic coupling element 41 . in the end region of the double - eccentric shaft 15 projecting past the end of the adjustment shaft 14 , there are two axially offset , eccentric peripheral surfaces 16 , 17 , which each carry an anti - friction bearing 18 , 19 . the two extremities ( regions of maximum distance of the peripheral surfaces 16 , 17 from a longitudinal axis x - x of the camshaft adjuster ) of the peripheral surfaces 16 , 17 are offset by 180 ° relative to each other in the peripheral direction . the anti - friction bearings 18 , 19 each carry intermediate gears 20 , 21 on their outer surfaces . the intermediate gears 20 , 21 have several bores 22 , 23 distributed in the peripheral direction . a common connecting piece 24 passes through each bore 22 , 23 , with this connecting piece extending parallel to the longitudinal axis x - x of the camshaft adjuster 13 . the connecting piece 24 is supported in its end regions and outside of the intermediate gears 20 , 21 in circular ring - shaped support elements 25 , 26 . the double - eccentric shaft 15 passes with play through the inner bore of the support element 25 . the support element 26 is locked in rotation with the camshaft 12 on the inside in the radial direction . for this purpose , the support element 26 is connected with the camshaft 12 via a tensioning screw 27 , which is screwed into one end of the camshaft 12 . a housing 28 of the camshaft adjuster 13 has a hollow cylindrical wall 29 , which carries on the outside in the radial direction the drive element 11 , in particular a belt pulley , and which forms on the inside in the radial direction a ring gear 30 . in the region of the extremities of the double - eccentric shaft 15 , that is , on opposite peripheral regions , the intermediate gears 20 , 21 each mesh with the ring gear 30 . in the embodiment shown in fig1 , for the intermediate gear 20 , the extremity of the peripheral surface 16 is shown , so that the intermediate gear here engages with the ring gear 30 . the extremity for the peripheral surface 17 lies in the half - plane not shown in fig1 , so that the gearing of the intermediate gear 21 in the shown region does not engage with the internal gearing of the ring gear 30 . the bores 22 , 23 have an over - dimension relative to the diameters of the connecting pieces , such that relative movements caused by the extremity are possible between the intermediate gears 20 , 21 and the connecting piece 24 . another anti - friction bearing , here a needle bearing 31 , is connected between the head of the tensioning screw 27 and the double - eccentric shaft 15 . the camshaft 12 emerges from a cylinder head 33 under a seal through a sealing element 32 . the support elements 25 , 26 are guided via suitable sliding bearings relative to the housing 28 and are supported on the step for the ring gear 30 on the inside and also in the direction of the x - x axis on the outside by means of suitable securing elements 34 . if the adjustment shaft 14 is driven by the control drive at an angular velocity that deviates from the angular velocity of the camshaft 12 , then the extremity and thus the contact point between the intermediate gears 20 , 21 travels in the peripheral direction relative to the ring gear 30 . in this way , the angle between the drive element 11 and the camshaft 12 is changed . in terms of additional principle details of the construction of the camshaft adjuster with double - eccentric gear mechanisms , refer to the publication de 102 48 355 a1 by the applicant . the contact surfaces moving relative to each other and rolling in opposite directions and also the anti - friction bearings 18 , 19 , 31 are provided with lifetime lubrication . leakage of such lifetime lubrication from the housing 28 is prevented by the use of sealing covers 36 , 37 , which close both openings of the wall 29 . for the embodiment shown in fig1 , the sealing covers 36 , 37 rotate with the housing 28 . the sealing cover 36 is snapped into a suitable groove of the housing 28 . on the inside in the radial direction , a sealing element 38 is connected between the sealing cover 36 and the adjustment shaft 14 . a sealing element 39 is connected between the sealing cover 37 and the housing 28 . on the inside in the radial direction , the sealing cover 37 has a collar , on which on the inside in the radial direction a sealing element 40 is supported , which is actively connected with the cylinder head 33 on the outside in the radial direction . for the contact regions of the sealing covers 36 , 37 with the adjacent components both on the inside and also on the outside in the radial direction , for example , the following solutions are conceivable alternatively or cumulatively : the sealing covers 36 , 37 can be inserted or snapped into the adjacent components with a non - positive connection . here , the sealing covers 36 , 37 are pressed against the adjacent components through the elasticity of the sealing covers 36 , 37 themselves or additional elastic elements , whereby a sealing effect is produced . furthermore , the sealing covers can be held by the adjacent components with a positive connection , for example , in a groove . a sealing element , such as , for example , a sealing ring or a radial shaft sealing ring can be connected between sealing covers 36 , 37 and adjacent components . furthermore , a diaphragm seal or labyrinth seal can be used , which is adapted to the special operating requirements , such as , rotational speeds , centrifugal forces , and a viscosity of the lifetime lubrication , as well as the occurring temperatures . the sealing cover 36 is preferably supported in the end region on the outside in the radial direction against the wall 29 . alternatively , a support relative to the support element 25 is possible , wherein in this case an additional seal must be provided between the support element 25 and the wall 29 . on the inside in the radial direction , the sealing cover 36 is supported against the adjustment shaft 14 . alternatively , it is also possible that the sealing cover 36 is supported against the double - eccentric shaft 15 . in this case , it is to be guaranteed that the connection between the adjustment shaft 14 and the double - eccentric shaft 15 has a tight construction . the sealing cover 37 is supported on the outside in the axial direction against the wall 29 . alternatively , it is possible that the sealing cover 37 is supported against the support element 26 , wherein in this case , a seal between the support element 26 and wall 29 is to be provided . on the inside in the radial direction , the sealing cover 37 is supported against the cylinder head 33 or the camshaft 12 . for the case that the camshaft 12 and / or the adjustment shaft 14 does not project into the camshaft adjuster 13 , but instead is coupled outside of this adjuster to a shaft projecting out of the camshaft adjuster , a seal from this projecting shaft can be realized . the sealing covers 36 , 37 preferably have an inherently stiff construction , for example , as a sheet - metal part . alternatively , the sealing covers can have a construction that is at least partially not resistant to bending , especially as a sealing bellows , or the like . the sealing covers 36 , 37 can be completely left out for a different embodiment of the invention , as long as there is a seal between the housing 28 , support element 25 , connecting piece 24 , double - eccentric shaft 15 , and adjustment shaft 14 or housing 28 , support element 26 , connecting piece 24 , and camshaft 12 . according to another construction according to the invention , a rubber - elastic form element 41 is connected between the adjustment shaft 14 and double - eccentric shaft 15 . in this case , a seal of a sealing cover 36 from the rubber - elastic form element 41 or from the adjustment shaft can be realized . in some circumstances , it is sufficient in this case to provide a diaphragm seal here , because the lifetime lubrication is accelerated outwards in the radial direction due to centrifugal force . the camshaft adjuster used according to the invention can involve a camshaft adjuster of any type . for example , as a control unit , a construction with a bldc motor with rare - earth magnet and fixed stator , preferably with bipolar triggering , can be used . any other motor , for example , a brush - type direct - current motor , is also conceivable . furthermore , camshaft adjuster units , for which the motor rotates with the gear mechanism , can also be used . a rubber - elastic form element 41 can be integrated into the adjustment shaft 14 as a coupling element between the adjustment shaft 14 and the electric motor , wherein , however , other possibilities , for example , a feather key or a splined shaft profile , can be used . in addition to the described double internal eccentric gear mechanism , other gear mechanisms , for example , single internal eccentric gear mechanisms , swash - plate gear mechanisms , shaft gear mechanisms , planetary gear mechanisms , and other high transmission ratio gear mechanisms can be used in a known way for belt - driven internal combustion engines . the lifetime lubrication is preferably embodied as a lifetime grease filling . other lifetime lubrications , such as motor oil ( such as the type for gear mechanisms with chain - driven motors ) are also conceivable , wherein in this case , increased sealing requirements are to be set .