MXPA00004118A - Drive train - Google Patents

Abstract

The invention relates to a drive train, especially for motor vehicles, comprising a drive unit with a drive shaft, an output unit and an electrical machine interacting therewith.

Description

JO¬ FIELD OF THE INVENTION Field of the Invention The invention relates to a drive train or rope, especially for motor vehicles, which includes a drive unit, such as a combustion machine, with a drive shaft, a stopping unit with a drive shaft. input, as a transmission mechanism with transmission input shaft, as well as at least one electrical machine in connection with the action of the drive rope and with at least one coupling arranged in flow of force between the drive shaft and the input shaft or armature shaft of the stopping unit, which allows the coupling process and uncoupling of the drive unit of the power take-off unit. BACKGROUND OF THE INVENTION Such installations are known as hybrid drives with an electric motor and a combustion engine by DE-OS 32 30 121 or as internal combustion engines or with a running generator by DE PS-41 12215. The arrangement of the electric machine is made according to the requirements either coaxially around the axis of rotation of the combustion machine - as for example known by the DE-0S-33 35 923 - or in relation to its axis of rotation parallel to the rotating shaft of the internal combustion machine comes presented in the FR-OS 81 19324. In order to be able to use the limited moment of rotation of the electric machine during the start-up process, as a rule the effect connection, which can be a belt drive, a belt pulley arrangement, a pair of gears or similar, is transformed, since the electric machine rotates more quickly than the driven unit, for example the combustion machine. As soon as the combustion machine is in operation and the electric machine is driven as a current generator, it is advantageous that the electric machine has an ideal transformation to improve its degree of efficiency, which makes it necessary to use a mechanism. For this, in the patent DEPS4H2215, an arrangement is proposed with a planetary gear where the transmission is controlled from outside is performed with a coupling connected to an additional necessary footprint engine, whereby control and transmission agents increase the weight and the cost. SUMMARY OF THE INVENTION It is the task of the invention therefore to improve a driving rope of the type described, in such a way that * - > 4 - . 4 -, z active connection between the electric machine and the drive shaft between the drive unit and the power take-off unit or at the opposite ends of the drive shaft make it operate as an auxiliary aggregate in a known manner, where it can also be advantageous a band drive for multiple secondary aggregates in relation to the electric machine. The active union can be formed by a pair of transmission discs, which are joined one with the other by a friction closure, by a wrapping means. thus the transmission discs can be provided as known transmission belts and the wrapping agent can be a band or can advantageously be provided especially for the transmission. transmissions of moments large pairs of conical discs, where as a wrapping agent a chain forms the friction closure between the two conical disc wheels. In addition, the action joint may be formed of at least one pair of gears or wheels of friction coupled to one another, where an effect connection can also be advantageous, which for each transmission stage provides a separate pair of gears or a pair of separate transmission discs, with the corresponding enclosing means. 25 The drive train according to the invention, can suitably be applied in such a way that the electric machine is used at least as a gear or resistor, however advantageously other uses can be provided, for this, for example, the power characteristic of the electric machine can be established in such a way not only work as generator and gear, but it can also introduce a turning moment in the power take-off unit, if necessary up to an extraordinary operation of the vehicle with the electric machine. As a power take-off unit, for example, a speed change gear can be provided that can be uncoupled at least by a switching coupling of the drive unit where the electric machine advantageously in connection with the drive unit is uncoupled from the take-off unit. of power, however that in any given case also a connection of action can be provided with the gear of change of speed, where the drive unit can be uncoupled from the electric machine and the gear. Especially, such arrangements are possible if the electric machine and / or its gear, must be placed under the gear to improve the use of its degree of action either spatially and / or functionally where the start-up process can take place advantageously in a Vacuuming of the gear change gear. The electric machine can for this be coaxially co-ordinated around a gear input shaft or around its own shaft that is in connection with this action, it is also spoken of a connection or effect between the drive unit and the electric machine, then also the connection of action between the power take-off unit in the form of the occurrence of the gear input shaft in action with the electric machine, and of the electric machine in this embodiment example is implied. Furthermore, it can be advantageous to uncouple the electrical machine between two switchable couplings of the drive unit as well as the power take-off unit to use the oscillation effect useful in the electric machine that rotates freely for energy gain. and / or to obtain a turning moment necessary for the driving of the drive unit where the electric machine can have an oscillating or inertial mass coordinated in the drive shaft, for example an inertial wheel. According to the thoughts of the invention it is advantageous to equip the connection between the drive unit and the electric machine with a gear that allows a better adjustment of the number of working revolutions of the electric machine in the degree of efficiency in the different demands of this and the switching from one transmission stage to another automatically controlled by the gear, where it may be advantageous to provide a multiplicity of transmission stages. However, in particular, a simplified embodiment with only two gear stages can be advantageous due to the low construction cost. For this, in a use of the electric machine as a start-up generator, as well as an apparatus that pushes the driving unit and that can generate electric power, a first transmission stage for the running process and a second stage for the process will be provided. of the generation of electric power that will be properly the mode of operation. The first transmission stage converts the number of revolutions of the electric machine to a slower speed of the drive shaft, so that a higher torque is produced and the necessary start-up time can be reached. The second transmission stage during the operation mode causes a slower transmission, so that the number of revolutions of the drive shaft, with respect to the shaft of the electric machine is less or equal, that is, the Transmission ratio of the electric machine to the drive machine can be in the range between 1: 2 and 2: 1. Advantageously, the connection of action can be established in such a way that no transmission at this stage is effective. For the first transmission stage, the transmission range can be between 3: 2 and 7: 1, which will be especially advantageous. Given the case, it may be advantageous to provide a constant proportion of predated transmission, for example in a range of 3: 2 to 5: 1, which places the number below with respect to the electric machine, so that the number of rotations of the motor with respect to the number of rotations of the electric machine is decreased by the corresponding transmission factor, this constant transmission can then cover the two transmission stages. For the adjustments of the variable transmission stages, gears of all types can be used, for example stopping or rotating advantageously, the active connection can be formed by belt drives, pairs of gear wheels, friction wheel pairs, drive chains and the like, where in a constant gear, the action joint can be formed by at least one pair of gears or gears. The control of the transmissions is made through a combination of couplings and free wheels, which in the gear release or block certain combinations of sprockets or force paths, where the couplings that in the place of application to increase the number of rotations are closed or open, not controlled from outside, but can be advanced or go back by centrifugal forces. An example of an embodiment with an electromagnetic coupling which is controlled by electrical signals generated dependent on the number of rotations of the driving generator is also advantageous. thus, for example, a combination of two freewheels or a coupling and a vacuum operation or two couplings in two different transmission stages can be switched. The mechanism can come into action, especially by the direction acting with the moment of rotation with a variable number of rotations on the gear proper in the process of starting the electric machine and during the operation of the drive unit, adjust in that way its transmission, where the vacuum operation is carried out for the second transmission stage if the moment of rotation of the electric machine is introduced during the start-up process and a second vacuum operation is established for the first transmission stage if the moment of rotation of the unit Impeller is introduced during operation. An advantageous mechanism according to the invention can consist, for example, of a planetary gear wheel with a sun wheel, at least one planetary wheel and a hollow wheel, where the wheel is fixedly attached to the box, the rods are likewise fixed in rotation with the electric machine shaft, where in the flow of force between the rods and the electric machine and the wheels of the planetary and the electric machine is available each time for a transmission stage a free wheel or a coupling . Another conformation according to the invention, provides an axially displaceable hollow wheel, where the first transmission stage can be provided by the delay of the same when joining it to the box where the flow of forces from the sun wheel fixedly linked with the electric machine can be transmitted through the planetary wheels to the rod for the drive element, and this causes a slower transmission and a second transmission by the union to the rod attached to the drive shaft, where here the transmission will be 1: 1 The axially displaceable hollow wheel can be controlled in particular by an inclined gear of the gear wheel of the planetary, so that in a flow * At the moment of the electric machine to the drive unit through the applied moment, the axial hollow wheel can be displaced in the direction of the box and form a friction form and / or closure with it. Although the moment of rotation of the driving unit, the axial hollow wheel can be placed along the inclined gear in the direction of the surface of the rod forming the form and / or friction closure. For the formation of the form or friction closure, they can be provided in the surfaces of contact of the rod and the box, in addition to the correspondingly constructed means in the side walls of the hollow wheel, such as for example cams or an enclosing gear. Supported additionally or alone, also means such as friction surfaces can be used with corresponding friction coatings where the friction surfaces can be applied to the hollow wheel or to the rod or to the box. In addition, advantageous for boost operation of the electric machine, ie a support of the drive unit by the electric machine during the forward movement of the vehicle during which the moment flow of the electric machine does not have to change in the direction of the power take-off unit , as in the start process, is the retention of the first stage of transmission, special? to &róie numbers of revolution that are greater than during the start process. For this, it can be provided that at least one body placed on the outer periphery of the rod in a recess when high revolutions are presented by means of the increasing centrifugal force grip in a correspondingly arranged hole in the inner periphery of the hollow wheel, with which produces a form closing and the transmission stage is blocked, although by the boost operation the moment of rotation direction can be reversed. Advantageously, a multiplicity of bodies distributed in the periphery can be provided, for example having a spherical shape or they can be rounded rods, where the edges of the recesses on the hollow wheel sides can be rounded both axially and radially. Advantageously, it is also to support the spheres with a spring force that adjusts according to the need against the centrifugal force. Similarly, a mechanism can be constructed each time from a pair of sprockets for each transmission stage where the sprocket pairs can be controlled by the coordination of freewheels and corresponding couplings. thus, for example, in two transmission stages provided by each transmission stage, a coupling or a free wheel. further, according to the idea of the invention, it can be advantageous to have an embodiment that has two pairs of axially spaced transmission discs with different diameters of transmission discs for the adjustment of two transmission stages, where the transmission discs can present each time a separate enclosing or surrounding agent, being mounted on the drive shaft and the shaft of the electric machine and provided for each pair of transmission discs a vacuum and where the two free wheels are against with respect to their direction of overriding or to ignore it. The spatial arrangement of the mechanism can be carried out for reasons of place in electrical machines arranged coaxially radially inside the rotor, where the fixed hollow wheel can be formed from the stator. It is also advantageous in electrical machines with a start-up shaft of different ratio of the starting shaft of the drive machine having an action connection with two disc-shaped transmission elements, for example transmission discs, discs of friction or gears perform the arrangement radially within those transmission elements selectively on the side of the unit booster or on the electric machine, with which small diameter electric machines can be manufactured. The box of the electric machine can be placed in a gear arrangement radially inside the band disc provided on the side of the electric machine, simultaneously with the hollow wheel for the mechanism and the transmission elements can separately form the fixed transmission . Another embodiment of the idea of the invention seeks the use of a damping device between the electric machine and the drive unit, where these can be placed between the driving unit and the electric machine and in an especially advantageous manner between the gear and the drive unit. Here it is a constructive form in itself known to be conformed according to the invention for use in the object of the invention, so for example in the arrangement of the gear can be placed on the axis of the electric machine radially inwards of the rotor or in a positioning of the gear selectively next to the drive unit or next to the electrical machine radially inwards of the parts forming the action joint, for example radially inwardly of the transmission discs or the gear wheels.

The meanismoe are, according to the idea of the invention, fixed with their box in the box of the electric machine or in the drive unit. It can also be advantageous, especially if it is to be avoided in the arrangement of fastening agents to place them on the side of the driving unit or of the electric machine, by pivotally mounting the box around the fixing shaft, for example of the drive shaft. or the tree of the electric machine. The assembly on the drive shaft will be explained by way of example, implicitly the corresponding assembly on the shaft of the electric machine is also implied and it can be advantageous depending on the circumstances of the application, especially on the conformation of the construction space. This type of gear or mechanism is statically indeterminate and can according to the inventive consideration be provided in such a way that the box is mounted on the drive shaft in a rotatable manner, where the box has a lever arm in the direction of the surrounding medium, in which a tensor of the surrounding medium is arranged. On this the box can be supported depending on the moment of force applied by the surrounding means and thus cares for a tension of the surrounding environment dependent on the moment, where it advantageously presents a base tension. It is particularly advantageous if the assembly of the mechanism box and / or the transmission disk is provided by means of roller bearings or the like at the same axial height of the surrounding means, in the plane of the surrounding medium or band, since in this way the bending forces on the bearing or support will be negligible and the duration of the support can be extended. For a production of the optimum mechanism from the point of view of cost-also in other examples of embodiment-a simple conformation of the bearing can be made, for example as a sliding bearing, by the use of bearings of synthetic material or the like, for the passage of transmission for the start of the drive unit, since this process is comparatively cut with respect to the operation as a generator and therefore matters little with respect to wear. Another possibility of shaping a bearing or support statically indeterminate can be the separation of the axis of the transmission disk and drive shaft, where both are joined by a force closure, for example by a pair of gear wheels. For this purpose, the mechanism housing can be mounted on both pivots and the mechanism installed around the drive shaft. In an application on the torque mechanism, the transmission disk is deflected around the pivot point of the drive shaft, however, it is supported by the tension of the surrounding environment. The distance d between the axis of the transmission disk and the axis of the drive shaft is then selectable so small that by observing a safety factor, the axis of the transmission disk can be prevented in a complete rotation that performs a slip. The distance d previously selected is proposed in the first line by the construction mass, so that a distance d with the condition 20cm >; d > lcm is especially advantageous. In this exemplary embodiment, planetary mechanisms can be advantageously used, also with an axially movable hollow wheel as described above. According to the inventive thinking, statically indeterminate gear mechanisms can also be formed when, for example, two pairs of gear wheels are coordinated in such a way for two transmission stages that the gear wheels by means of freewheels move against each other in reference to the overdraft direction, can be mounted on the drive shaft and the gears or gears corresponding thereto are joined in a force closure with the transmission disk, which again is arranged with an axial displacement to the drive shaft. Also here the transmission disk is supported against the surrounding or enveloping medium. Advantageously, it may further be that the essential constructional parts of the driving rope, for example the mechanism and / or gears of the mechanism are made of metal and / or synthetic material or a combination of both. In addition, some parts such as boxes, covers and / or flanges can be stamped, pressed or molded and / or stamped deep. In addition, it may be advantageous, according to the requirements of the manufacturing conditions, to use screws, bolts, welds and / or reinforcers as connecting agents. In accordance with the inventive thinking, it may be advantageous especially to place the electric machine on the side of the drive shaft about this coaxially which was originally provided on the side of the disk of the belt. The arrangement of the machine on this side of the drive shaft contrary to the speed change mechanism, offers in conjunction with corresponding embodiments general advantages with respect to arrangements parallel to the axis on this side and / or coaxial arrangements of the electrical machine axially between the drive unit and the mechanism. Thus, for example, the rotor of the electric machine with its mass can perform the oscillating function in the moment of inertia so that the oscillation wheel arranged on the mechanism side, for example in a switching gear, up to the friction surface of The coupling can disappear, where an effective extinguisher in the drive rope can be provided in the area of the electric machine or at the end by the drive shaft mechanism side. A torsional oscillation damping device can be advantageously connected in the flow of force between the drive shaft and the rotor of the electric machine, so that it is largely isolated from the torsional oscillations and / or the torsional load of the torsional oscillation. Drive shaft can be reduced in the torsional oscillations by the existing rotor mass by means of decoupling. Here it can be particularly advantageous to place the torsion oscillation damper in a supercritical oscillating insulation, wherein a mass coordinated as energy storage effective in the peripheral direction with respect to the rotating mass as a secondary mass and directly to the drive shaft, for example, an optimum inertia wheel with respect to the required mass can be applied and there both can be relatively rotatable one against the other and with this having an inertial effect of two masses known per se by acting with the positive properties already mentioned, where the number of resonance rotation of the driving rope can be placed in an area below the number of rotations ai empty and with this out of the field of travel. It may also be advantageous for the damper only to operate in a section of the operating zone of the drive rope, for example in a pre-determined transmission stage between the drive shaft and the rotor and / or during a certain operating mode, for example, in advance operation and not during the start-up of the operation unit by the electric machine. In addition, it may be advantageous to operate a crankshaft extinguisher parallel to the shock absorber. In addition, the rotor mass can be used as an extinguishing mass in another embodiment. Here the resistance to rotation and the damping of the connection between the rotor and the drive shaft can be determined with the respective proper frequency of the drive shaft. It may furthermore be advantageous to provide a mechanism or gear between the rotor and the drive shaft in the constructive unit with a crankcase extinguisher and a torsion oscillation damper, where the constructive unit may be partially filled with a lubricant such as oil or grease and the component parts can work under continuous lubrication. Here it can be of advantage to realize the gears of the mechanism of the torsion oscillations to get to obtain a poor operation of noise and to improve the duration of the vehicle. A mechanism or gear between the rotor and the drive shaft with at least two gear steps can be connected in the embodiment according to the invention by automatically acting between the transmission stages, for example, by the inclined gear wheels which they produce a deviating force, by a centrifugal force adjustment, by a freewheel or the like. Another alternative is the active switching of the mechanism from the outside when, for example, the pitch or speed wheels are locked and / or joined by means of magnetic couplings, magnetic brakes, for example gripping couplings operable by magnetic switches and / or by friction couplings operable by actors, so that by the combination of the operating states different transmission stages can be realized. For the synchronization of the automatic or externally caused switching processes, corresponding synchronization agents such as blocking rings and the like can be used which allow a change-dependent switching of the number of rotations and / or the electrical machine can be used by an active control for adjusting the number of synchronization rotations. For this purpose, the electric machine can be adjusted, for example, before switching from a transmission to a faster one, that is, from a high number of rotations of the electric machine to a low number of rotations in its power supply, so that the During the synchronization process, the machine that rotates more quickly from the construction part that forms the form closure of the new transmission of the mechanism, can take it to an approximately equal number of rotations. In the same way before switching to a slow transmission, the load of the electric machine, and with this its number of revolutions can be regulated to higher, for example by a short time switching of uses, so that the difference of The number of rotations of the two forming the new transmission stage can be kept to a minimum by the construction parts that form a closure by its figure, where the slip moment that is expected from the electric machine that now rotates lower is compensated or the electric machine for short time, act quickly as a driver on the constructive part that rotates more slowly. The power jump required for synchronization by the electrical machine, which can be in the range of one to several kW, occurs from the moment of synchronization with the number of synchronization rotations corresponding. Since in the synchronization the number of rotations of the constructive parts that cause the transmission stage according to the definition is similar, the load jump is at the beginning of the maximum synchronization. In a timing of predation by the type of construction of the coupling and switching elements, the fixed moment remains by the mass inertia of the masses to be accelerated and by the variation of the angular velocity which is a function of the transmission of the mechanism. The magnitude of the power acting by supporting the electric machine, may depend on its corresponding operating state, if this provides for example maximum load can not basically raise its generating moment. In this case, it can be advantageous to cause this by a collapse of the generator power, for example by disconnecting different users or by the power supply through the battery before the connection process, so the electric machine is artificially put in the position of synchronize to be able to apply suddenly a high moment, where the tension of edges of the network can be maintained through the charging voltage, so as not to limit other electrical users in their capacity of power. A weaker synchronization process can be achieved especially because, in order to form the shape closure of the two parts forming the transmission stage, the number of synchronization rotations is applied by means of the electric machine with a gradient as low as possible. This can correspond correspondingly in the change of a number of low rotations to a high one of the electric machine, where by means of the connection of additional users it elevates its moment "artificially" to in the connection (to remove load), here it can even be reached a even greater effect that the electric machine changes to the operation as a motor. A high load or power jack can also be achieved because machine E is intentionally operated with a bad efficiency rating. In order to make the switching process as smooth as possible also with more rapid variations in the number of rotations for the user, it is further proposed that the number of switching rotations during operation, that is, the operating mode varies. For example, engines with a waste gas side turbine loader can place the number of switching rotations in the number of rotations, in which the kinetic energy of the waste gas sets the nominal load pressure, so that Increased acceleration at the end "of the turbo hole" is used for the switching process and with this the electrical losses during the synchronization can be compensated. Advantageously for a drive rope, especially for a drive rope according to the thought of the invention is the storage of mechanical energy in the drive system during the lag processes, where mechanical energy can be mechanically stored, for example as rotating energy in an oscillating wheel, for example in the rotating mass and then an available accelerating process in progress of the internal combustion engine and / or by means of a conversion is stored in electrical energy. It is proposed, for such concepts in which also in the recovery phases the drive shaft of the drive unit rotates as an internal combustion machine, for example if the electrical machine is not uncoupled by means of a collection of the combustion machine, to reduce the driving moments of the driving unit by the following advantageous measures which are applicable individually or in combination during thrust operation. Reduce the loss due to lack of hermeticity and change of load due to the forced opening of the valves in the transversal operation. This can be done in electromechanical valve drives, hydraulic and pneumatic electromagnetic, but mainly the application of a mechanical adjusting member may be advantageous. The reduction of strangulation losses by opening the throttle hood, for example by means of existing adjustments in the transport with "E Gas". Reduction of the friction load of the auxiliary aggregates, for example by the application of electric pumps and electric water driven by bands. Oil and water pumps can be operated controlled by the characteristic field in the electrical operation, so that they work with minimum losses during the push. Application of a valve operation that is not driven directly by the crankshaft, and thus the disappearance of the friction in the disconnection in thrust operation. Limitation of drag power that increases strongly with the number of rotations of the motor by a transmission adjustment. For example, a convenient transmission position can be realized through a stepless mechanism (CVT branched hybrid charging operation) by automating the stages or with automated manual switching operation where the adjustment of the transmission can be made in order to load of low drag depending on the transmission of the electric machine and the optimum operating point that emerges (number of operating rotations), where the determination of the optimum transmission can be made with the consideration of both magnitudes in a control unit. The reduction of the power of drag or slip in the phases of push by the commutation or the limitation of taking of load of the auxiliary aggregates and of the users, as long as they do not serve the security of the transport or are immediately remarkable in the aspect of For example, convenience, for example electric heating, air conditioning compressors and the like, it may be advantageous for the user to cross-connect it through a common cutting position (for example via CAN) for example in an objective way to connect or disconnect by means of a control unit. control the use. From the energetic point of view, the combustion engine can then, during its operating phases, operate under high average pressures with a specifically low fuel consumption. For the drive train with a running generator and a combustion machine in which these aggregates for example for cost reasons are not uncoupled from one another by means of a coupling, it may be advantageous to increase the recovery load so that the moment of dragging or pulling power of the combustion machine is reduced by at least one or a combination of the following characteristics: decrease of compression losses and / or expansion; decrease in load change losses by minimizing the resistance to current in the control and throttle organs in thrust operation; reduction of the friction load due to the application of the internal combustion engine of independent secondary aggregates, for ple oil and / or water pumps or at least valve operations that in the operation of the handwheels are not driven by the machine internal combustion; disconnection of uses that are not absolutely necessary, for ple electrical heating and the like. It can be advantageous here to reduce the losses due to lack of hermeticity and change of load by forced opening of the valves in the thrust operation by means of an electromechanical, electromagnetic, hydraulic or pneumatic adjustment member, mainly also by an adjustment member Mechanical for actuating the valves at least in thrust operation, throttling losses can be decreased by opening the throttle cover with an automatic throttle adjustment such as E-Gas. The friction load of the electrically operated secondary aggregates can be operated poorly in losses correspondingly in the thrust operation by means of a controlled operating mode in a known field. The friction load of the valves may disappear with the disconnection during thrust operation. The sliding power increases as a rule as the number of revolutions of the combustion machine increases, so that it may be advantageous in the thrust operation to carry out the transmission of the mechanism, for ple, of an automatic cap mechanism manually or automatically switched, CVT or a hybrid mechanism of load branching in the direction of a large transmission (overdrive) where the transmission can be made in coincidence with the optimal operating point of the electric machine and both parameters can be adjusted by means of a corresponding control in reference to the excellent transmission adjustment from the economic point of view. The taking of power to a total disconnection of secondary aggregates and uses that do not directly serve the safety of transport or that do not become directly noticeable with respect to comfort, can be advantageously controlled by means of a communication system central, for ple a CAN-Bus where the use of the current is regulated as a priority or can be switched on or off, so that the combustion engine during the operating phases under high average pressures can operate with specific low fuel costs. BRIEF DESCRIPTION OF THE FIGURES The invention will be described in more detail in relation to figures 1-21, here they show: FIGURE la-d, different possibilities of arranging a driving rope according to the invention; FIGURE 2, a section of a mechanism according to the invention arranged in the shaft of the electric machine with two free wheels under vacuum; FIGURE 3, a section of a mechanism according to the invention arranged in the shaft of the electric machine with a free wheel and a coupling; FIGURE 4, a section of a mechanism according to the invention mounted on the crankshaft; with two pairs of transmission discs of different diameter; FIGURE 5, a section of a mechanism arranged in the drive shaft with a hollow wheel displaceable axiomatically; FIGURE 6, a section of a mechanism mounted indefinitely in a static manner disposed in the drive shaft with an axially displaceable wheel; FIGURE 7, a schematic view of a pair of transmission discs with tensioning apparatus; FIGURE 8, a section of a rotation mechanism mounted on a crankshaft with a drive disc on the drive shaft side displaceable on the shaft to the drive shaft; FIGURE 9, a basic scheme of a front wheel mechanism mounted on the crankshaft with ur. transmission disc on the drive shaft side displaceable on the shaft to the drive shaft; FIGURES 10 to 17, other conformations and possibilities of arrangement of the shaped objects according to the invention; FIGURE 18, an exemplary embodiment with an external block of the transmission steps; FIGURE 19, another embodiment with a mechanism arranged in the drive shaft with an improved degree of action; FIGURE 20, an example of an embodiment with an electrical machine arranged concentrically around the drive shaft; FIGURE 21, a detail of the arrangement presented in Fig. 20; FIGURES 22 and 23, examples of embodiment of an electric machine integrated in a mechanism; and FIGURES 24a-24c, procedure for controlling an electrical machine during recovery. Detailed Description of the Invention Fig. Ia-d, shows different possibilities of arranging a driving rope according to the invention, i, i ', i ", i"' with a drive unit 2, 2 ', 2", 2"'for example a combustion engine with a drive shaft 3, 3', 3", 3"'which by means of a coupling 4, 41, 4", 4"1 is engageable with the input shaft 5, 5 ', 5' ', 5'1', of a power take-off unit 6, 6 ', 611, 6"' 'for example a mechanism such as switching mechanism, automatic cover mechanism or continuously adjustable mechanism (CVT) By means of an action joint 7, 7 ', 7", 7"', which transmits the moment that is presented and a mechanism that automatically switches in dependence on the direction of moment of rotation 9, 9 ', 911, 9'1 * is an electric machine 8, 8 ', 8'1, 8'1' in the embodiment examples of Figs la-c, connected to the drive shaft 3, 3 ', 3' ' and in the example of embodiment in the Fig. le, with the tree of In the exemplary embodiment of FIG. 1, the connection 7 between the coupling 4 and the drive unit 2 is arranged around the drive shaft 3 and transmits the torque that arises from the drive unit 2 through the mechanism 9 to the electric machine 8 and vice versa when the electric machine 8 produces the moment of rotation. In an exemplary embodiment not shown, the gear mechanism 9 is arranged in the drive shaft 3 and the action connection 7 is connected directly to the shaft 8a of the electrical machine 8, in a turn lock. The electric machine 8 is connected directly by means of the fastening 8b, with the driving unit 2 or with another construction part that is fixed to the vehicle (not shown), where the driving rope i is installed. The action joint 7 can be formed as a web drive, with corresponding bands and band discs, as a drive with tapered disc wheels and a wrapping agent, for example a chain or as a friction transmission or gear wheels or the like. The mechanism 9 can in a manner not shown be fixed on the electric machine 8 or on the housing of the driving unit 2 or on any other fixed part of the vehicle or be supported as a mechanism not statically defined with its housing or a lever constructed by an extension of shaft between the drive shaft 3 and the axis of the mechanism in the action joint 7. Fig. Ib shows an identical drive rope 1 'with the drive rope l except for the following differences: the electric machine 7 is arranged in this exemplary embodiment at the end of the opposite drive shaft 3 * of the power take-off unit 6 'by means of the action joint 7'. The self-switching mechanism 9 'is here placed in the drive shaft 31 and can also be provided in an exemplary embodiment not shown around the axis of the electrical machine 8'.

The embodiment example shown in FIG. 1, carries the electric machine 8"concentrically around the drive shaft 3" in a foflow between the coupling 4'1 and the drive unit 2 * where the stator 8a " fixed in the housing of the drive unit and the rotor 8b is a constituent part of the mechanism 9"which is formed radially inside the rotor 8", with an action joint 7'1 is produced for example by friction wheels and / or toothed with the drive shaft 3 * 'It is understood that an electrical machine 8' 'arranged coaxially around the drive shaft 3'1'1 - as already in US Patent 4,458,156 is published which is fully taken in this document it can also be placed at the end of the drive shaft opposite the power take-off unit 6"and in accordance with the invention, has a corresponding mechanism 9'1 for adjusting the transmission between the electrical machine 811 and the unit impulse 2'1 radially inwardly of the outer periphery of the rotor 8b ''. The advantage consists in the disappearance of large variations in the cutting position between the drive unit and the power take-off unit 2 '', 6 * ', for example in the bell of the mechanism. In Fig. Id, an embodiment is shown whose self-switching mechanism '*' is integrated in the power take-off unit 6 '' ', for example in a gear change mechanism. Here, too, you can - following the example of F gs. Ib, place the mechanism 9 '' 'around the input shaft 5' * 'or around the shaft of the electrical machine 8' ''. As a connection of action 7 '' ', it is recommended here, together with the described examples, preferably a pair of gears that can perform other transmission functions in the mechanism in particular. Such an arrangement can advantageously provide that the electrical machine can be connected directly to the input shaft of the mechanism or also be connected to it in a foclosure through an action joint. Here, it can be particularly advantageous to arrange the uncoupling electric machine of the combustion machine by means of a coupling, as well as another coupling between the mechanism and the power take-off, where the couplings will depend on the usual conformation of the mechanism and can be coupling friction and / or form closure. In Fig. 2, a partial view of the upper half along the axis 110 of the electric machine is shown which is not shown, in an embodiment of a mechanism 109 according to the invention, which is embodied as a planetary mechanism with a sun wheel 113 stamped or embedded in the shaft 112 of the electric machine, a planetary seat 114 and a hollow wheel 116 patterned on the inner periphery of the mechanism case 115 or fixedly attached to the case 115. The train planetary 114 is taken by a rod 117 with one of the number of planetary wheels of the planetary train or assembly 114 corresponding number of axes 118 on which the planetary wheels are mounted. The rod 117 has a radially extending flange part 117a for mounting the axles 118 and an axially extending sleeve 117b for mounting on the shaft 112 of the electric machine. In the embodiment shown, two bearings 119 axially spaced apart by a spacer ring 119a, which are secured on both sides each by a safety ring 119b, 119c, are provided for the rotatable and free nutation assembly. end of the flange part 117b opposite the radial flange part 117a, the rod 117 is disposed on its outer periphery of the first free wheel 120, on which the band disk 121 belonging to the electrical machine is mounted, where the freewheel 120 is pressed against a shoulder serving as stop 121a on band disk 121 and is secured on the opposite side with a locking ring 12ib against axial displacement. On the side of the band disk 121 opposite the planetary 114 is received at its inner periphery with a decreased diameter of the band disk 121, the second freewheel 122 and mounted directly on the shaft 112 of the electrical machine, where it is secured against axial displacement on the one hand by a shoulder 112a, provided on the shaft 112 and on the other hand by the safety ring 112b. The band disk 121 is protected against axial displacement by the security rings 121b, 12lc. The friction surface of the band disk 121 which is provided with grooves 121 takes the band which is not shown, which transmits the torque that is presented from the electric machine to a band disk on the drive shaft side and also inver. The box 115 of the mechanism 109 is extended by the rod 117, so that the planetary 114 and the bearing 119 in a closed space are greased or can run in an oil bath, where the separation between the rod 117, the box 115 and the shaft 112 is sealed by the seals 124, 124, 125. With the box 115 are screwed inversely to the electrical machine a fixing flange or a fixing bow 126 which can also be riveted or welded, with which the mechanism 109 by means of recesses radially applied on the outside 126a is joined and centered with the electric machine. If a moment of rotation in the direction of the drive shaft is fed from the electric machine, then the second free wheel 122 is overturned and the moment of rotation from the shaft 112 through the planetary 114 to the rod 117 and from there through the the free wheel 120 on the band disc 121 is driven to be transmitted to the drive shaft, hence a slower transmission results, whereby the electric machine with a greater number of rotations and a correspondingly smaller moment can put on march to the driving unit. To support this process, a slow transmission can also be provided by the selection of the diameter of the band discs. In a moment of rotation flow from the drive unit in the direction of the electric machine, the torque is driven from the band disk 121 directly on the freewheel 122 to the shaft 112 of the electric machine and drives the machine without transformation. this operating mode can generate current. Here the freewheel 120 is overlapped. Fig. 3 shows with the mechanism 209 a variation of the mechanism 109 with the use of a coupling 220 which is controlled by an electro magnet 227, instead of the first free wheel 120 in Fig. 2.

For this purpose, the electromagnet 227 is surrounded by an annular core 229, which is fixedly connected to the housing 215 and has a snap connection 228 on its outer periphery, which feeds the magnet 227 with an external current source and a conduit. of control that for example opens and closes the electro magnet 227 depending on the current direction with respect to the electrical machine. The core 229 is mounted rotatable on a coupling flange 231, by means of the bearing 231, which on both sides is secured against axial displacement by the safety rings 230, 230b. The coupling flange 231 is centered on the shaft 212 and by means of an adjusting spring not shown, which it seizes in a groove 212a of the shaft 212 of the electric machine is attached for rotation. A radially directed part of the coupling flange 231 forms the pressure plate 23 of the coupling 220 and carries on the front side in the area of the outer periphery couplings 220a, which when coupling the coupling 220 with the couplings 220b provided on the side front of the pressure plate 233 centered on the shaft 212, will form a force closing gear. t ± The pressure plate 233 is moved during the coupling process of the coupling 220 with the action of the electromagnet axially towards the pressure plate 23ia, where during the above, the pressure plate is magnetized by means of the space 227a. The pressure plate upon disconnection of the magnet 227 is returned through a force feeder that acts axially and is not shown. In another course of the force flow is the pressure plate 233 by means of a gear 233b stamped on the inner periphery of an axially displaceable nose 233a axially displaceable and has a rotation lock with the sun wheel 213, which by means of a Axially directed flange portion 213 on its inner periphery has a bearing 212b on which shaft 212 is mounted, on the outer periphery of flange portion 213a a ring gear 213b meshing with the planetary seat is provided. The shafts 218 for the planetary seat are directly connected to the pulley 221 which thereby simultaneously forms the rod for the planetary seat 214. At the axial height of the planetary seat 214 is the case 215 radially widened and forms with an internal gear 216 the wheel hollow of the mechanism 209. The pulley 221 is mounted by means of the support 219 and the free wheel 222 which is axially secured with the safety rings 221, 22ic also on the shaft 212. The box is sealed against the shaft 212 and against the pulley 221 by means of the seals 223, 224, 225. The coupling being closed, for example during the start-up process of the drive unit. , the free wheel 222 is rotated and through the sun wheel 213 of the planetary seat 214 and the pulley the drive unit is started with a number of rotations of the electrical machine transformed to slow. If the number of rotations of the driving unit increases, then it can be exactly defined, for example, in the current reversal in the electric machine, the coupling 220 is retracted and the torque that comes from the driving unit is fed directly by the free wheel 222 and without transmission by the mechanism 209 to the shaft 212 and drives the electric machine. In Fig. 4, there is shown a partial view of an embodiment which refers to a mechanism 309 with an automatic adjustment of two transmission stages depending on the direction of moment of rotation with two pairs of pulleys each connected with a band with different transmission, where only the mechanism 309 is represented with the pulleys 321, 334 that belong to the pairs of pulleys. A flange 331 of the axially extending mechanism 309 annularly is connected by means of a radially internally directed flange at its inner periphery in the central region between both axial ends on the drive shaft 303 of the drive unit by means of of the screw 303a, where the turning connection between the flange 331 and the drive shaft 303 is produced by means of the gear 303b. A first annular part 33ib of the flange is directed on the drive shaft 303 and a second part part 331c is axially directed in the opposite direction to the drive shaft 303, whereby an annular plate shape is formed on the periphery external of the flange 331, where the first freewheels 322a, 322b and the bearing 319 are arranged axially between the freewheels and is secured by means of the safety rings 319a, against axial displacement. Around the freewheel 322a radially disposed on the drive shaft 303 in the part 331b of the flange 331, a flange portion 321a is provided, with a disc portion 321 running radially outward in the periphery area. external takes by means of recesses distributed in the periphery and bolts 32lc an annular disc-shaped part 32ld that radially outwardly with an annular projection 321e axially molded against the drive shaft 303 takes the pulley ring 321f to receive the band by means of welding 32lg. The flange 32la and the ring-shaped part 32ld can also be made in one piece. In order to transmit the highest possible turning torque, it is arranged and centered on the free wheel 322, on the bearing 319 as well as on the outer periphery of the flange part 32la, another flange part 335 which on the front side is joined with the flange portion 321a by means of the screws 335a which are distributed approximately uniformly on the periphery. In a radially protruding shoulder 335, a bearing 336 is provided on the outer periphery of the flange portion 335 and secured by a securing ring 336a on which the housing 335 is mounted in a rotatable manner. To secure the housing against axial displacement and for its sealing, a cover sheet 315a is provided on its front side, which by means of screws 315b distributed on the periphery is fixed on a flange part 315c of the box with corresponding recesses that run radially outwards and the box is placed in the bearing 336 axially by means of an axially patterned nose 3l5d, and the box 315 is sealed against the flange portion 335 by means of the seal 324. The box continues to bring to an optimum state the use of the place the radial contour of the flange portion 335, 331 and is pulled axially at its greatest distance from the drive shaft 303 and forms a flange 337 formed axially in the direction of the drive shaft on whose outer periphery the freewheels 320a, 320b are disposed, which again take the flange portion 331c of the flange 331 fixedly attached to the drive shaft 303. By means of a shoulder 315e projecting radially there has been a formed in the central axial zone of the box contour 315, a stop for the band disk or pulley 334 which is formed of an annular disk-shaped portion 334a of the pulley ring 334b for receiving the band and a reinforcing ring 334, where the three parts are welded together with one another. The mechanism 309 operates in such a way that during a start-up process of the drive unit by the electric machine, a moment of rotation of the pulleys of the electric machine is fed to the two belts and applied to the pulleys 321, 334, on the side of the drive shaft the moment of rotation. The band disk or pulley 321 with its larger diameter compared to the pulley 334 allows in the equal diameter assumption of the pulleys of the electric machine a greater transmission of the number of rotations of the electric machine at a slower rate. Through the 32lb flange parts, The moment of rotation is applied to the flange 331 and then led to the drive shaft 303, where the freewheels 322a, 322b are closed and the freewheels 320a, 320b are overtopped. During operation of the electric machine as a current generator, the freewheels 322a, 322b are overturned and the freewheels 320a, 320b are closed, so that the torque that comes from the drive shaft 303 is transmitted by means of of the flange 331, the freewheels 320, 320b to the box 315 and from there to the pulley 334. The small diameter of the pulley 334, in comparison with the pulley 321, produces a greater number of rotations than the electric machine, where the ratio of the diameters of the pulleys of the pulley pairs is observed for the determination of the transmission ratio, where in both stages of transmission a basic transmission of the same type can be established. In FIG. 5, an exemplary embodiment of a mechanism according to the invention 409 is shown, it is mounted by means of a carrier flange 438 on the drive shaft 403 and by means of the screw 403a that by means of a circular opening 413 enters the sun wheel 413. The box 415 is centered in the housing 402 of the drive unit by means of a flange portion 437 having in the cross section an L-shape, and is fixedly connected with it by means of the screw circle 402a. The axially extending branch 437a fits into a corresponding recess of the box 415, and by means of a gear 437b joins with the latter in a closure for turning. The box 415 is welded from the box parts 415a, 415b and 415c, however as the remaining parts can also be produced from parts manufactured in one part by means of modeling techniques and closes a chamber 445 in which the apparatus can be placed of damping 439 and the limiter 440, as well as the planetary mechanism 409a composed of the sun wheel 413 of the planetary wheels 414 and of the hollow wheel 416 rotatable and axially displaceable. At the outer periphery of the flange portion 415 a bearing 419 is placed against a radially formed shoulder 415d of the box part 415b and the flange part 415a which is axially fixed without play is fixed to a branch centered on the part of the flange portion 415a. flange 4i5a of a ring 419a opening in the U-shaped cross section to the bearing 419, which ring is secured against axial displacement by means of a safety ring 419b. In the bearing 419 is the contour of the box 415 with the formation of a minimum lumen 441 following the pulley box 442 consisting of the L-shaped flange 442, the pulley 421, intermediate ring 443 and the disc part 443, thus being rotatable with respect to the case 415 and secured against axial displacement by the internally directed nose radially in the flange portion 442a, and with the safety ring 419c-. The L-shaped flange 442a, carries on the outer periphery of the flange part radially directed outward the sheave with it welded 421 which is made as an annular component. In the connection to the pulley 421 an intermediate ring 443 is axially welded, with which the disc part 444 is screwed by means of the screws 444a. The disk part 444 has on its internal periphery a reinforcement on both sides 444b in the axial direction, where on the periphery distributed threaded holes for the screw of the sun wheel 413 which for this has a flange 413a directed radially outwards with the corresponding circle of holes to receive the screws 413b, with the above a connection and fixed sealing to the rotation between the sun wheel 413 and the disk part 444 is achieved.

The rod 417 of the planetary mechanism 409a takes the planetary wheels 414 by means of the axes 418 and the interimmediately placed sliding supports 414a, 414b and is rotatably mounted on an axially directed projection 438 of the carrier flange 438 disposed on the shaft. drive 403 by means of radially protruding shoulder 438b and safety ring 436 axially fixing the bearing 436. On the external periphery of the rod 417, a form closure for the damping apparatus 439 is provided by means of the toothing 446. principle of operation of the mechanism 409 having two transmission stages seeks a transmission of the number of rotations transmitted from the electrical machine to the band disk or pulley 421, for example during the commissioning process more slowly - with the basic establishment of the existing geometry 1: 5. For this, the moment of rotation of the pulley 421 on the disk part 444 is transmitted to the sun wheel 413. The sun wheel 413 drives the inclined gear 4l3e through the planetary wheels 413, which are preferably three. The rod 417 is blocked by the drive shaft 403 through the damping apparatus 439, so that through the inclined gear 416a whose inclination is selected so that the hollow wheel 416 with a force less than the opposite force of the drive shaft 403 acting axially and counter to, provided for the control of the transmitted moment of load, between the axially directed flange part 417a of the rod 417 and the hollow wheel 416 effectively, the three-part sliding bearing 449 is displaced with the ring radially acting spring 449a, the hollow wheel 416 is moved axially away from the drive shaft 403 and by means of the jaws 416a, 4l5d, forms a shape lock in the hollow wheel 416 and in the box 415. To insure against a deviation too strong of the hollow wheel, it has been fitted on the front side of the claw 4l5d, a safety ring 4i5e in the box part 415c. By means of the closing of form, the hollow wheel 416 remains fixedly connected with the box 415, so that the drive shaft with the corresponding transmission of the planetary mechanism 409a through the gear path 446 in the input part 447 with devices of application for the force feeder 448 to the outlet part 438c, in which the bags 438d have been formed to receive and apply the force feeder, with which the inlet part 447 and the outlet part 438 are rotatable relative to one another. against the other against the effect of a force feeder 448 that extends at least partially over the periphery to dampen the rotational formations that occur in the drive train. From the outlet part 438c, the moment of rotation is passed through the carrier flange 438 to the drive shaft 403, whereupon the drive unit is started with a reduced number of rotations compared to the electric machine. . Parallel to the damping device 439 there is a limiter 440 for limiting the rotational deformities by means of an annular part of mass 440, in which at least one pouch 440b has been stamped for the intake and application of at least one feeder force 440c, which extends at least partially on the periphery and against which effect the mass portion 440 is rotatable relative to the input portion 438d connected to the carrier flange 438, for example welded. If it reverses after the start-up process, the moment of rotation and now pushes the drive shaft 403, then the rod 417 moves against the moment of inertia of the electric machine, and the hollow wheel deviates due to the moment that it is applied through the inclined gear 416a axially in the direction of the drive shaft. To form a form closure with the rod 417, they have been provided on the front side in front of this, claws 416c gripping in corresponding window-shaped recesses 416b of the rod 417. To protect the grippers 416c from destruction since the switching in this form closure is carried out with the running rod 417 and the approximately immobile hollow wheel 416, a locking ring 450 is provided which is in connection with the hollow wheel 416 through a conical friction closure on its outer periphery and with a radiating nose 450a directed inwards, together with its internal diameter hung with play in a corresponding slot of the rod 417. With an approximately equal number of rotations between the hollow wheel 416 and the rod 417, the teeth of the axially directed gear 450b of the locking ring 450 catch, caused by the moment in which the inclined gear 416a occurs, in a 4l6d bored circle of the hollow wheel against the strength of the force feeder 450c acting backwards reestablishing and leaving that way l go the way for the formation of the form closure between the jaws 416c, 417b. When the moment flow is reversed, the gear between the parts 450b, 416d is released again by the axial distancing of the locking ring 450 and the rod 417, by means of the force feeder 450c.

After the formation of the form closure by means of the claws 416c and the recesses 417b the rod 417 rotates directly with the planetary settlement, since the hollow wheel 416 is locked with the rod and the torque flow passes without transmission through the axes 418 and the planetary seat 414 to the sun wheel 413, and from there by means of the disk part 444 to the pulley 421 that feeds the electric machine through the bands. In order to be able to use the electric machine as a booster, in order to support the drive unit or as the sole source of drive for the vehicle, it is desirable that at a number of revolutions that is greater than the starting speed, the switching to the transmission of gear in the moment flow from the electric machine. For this, a centrifugal force installation consisting of spheres, annular segments or rods 452 distributed on the periphery and sinking in the recesses 451 in the outer periphery of the rod 416 is used, which under the centrifugal force grip in corresponding recesses 453 in the hollow wheel and with a higher number of revolutions join firmly between the rod 416 and the hollow wheel 417. If the driving unit comes to a halt, they can enter a renewed process of starting the spheres 452 again free of force in the notches 459. To end the process, the edges of the recesses 449, 453 can be shaped correspondingly, for example profiles running correspondingly in the axial and peripheral direction can be provided or the spheres can be pressed backwards by means of small springs. In Fig. 6, a mechanism 509 is shown corresponding to the operation form and structure of the embodiment of the mechanism 409 of Fig. 5, in a partial view with the following different characteristics that will be described below. The 509 mechanism is not screwed with the box 515 to the driving unit, but is statically indefinite, this means that the moment of support of the box 515 by means of a lever 554 that extends radially along the pulley (not shown) of the electric machine and the pulley 521 disposed in the established plane of the pulleys, lever that is only indicated here, supports the band 555, whereby a variation of the drive unit box disappears and the mechanism 509 can be applied without major variation to the constructive form of the drive unit.

For this purpose, an axially reinforced bore 556 for a belt tensioning device 559 is provided on the end radially outward of the lever 554 by means of a shaft 556a, which by means of the bearing 556 receives a roller 556a. tension 557 rotatable to the 556a shaft. The tension roller 557 is supported according to the direction of the moment of rotation with a moment of support proportional to the applied moment of rotation on one of the two sides of the band 555, so that the band 555 with lower applied moments of rotation is less load and in this way it prolongs both its life and that of the supports or bearings 519, 558. The lever 554 is connected to the box 515 by means of a ring 554a modeled at its end axially in the direction of the box 515 having an internal toothing 554b in an axial projection 515 joined to the rotation with an external gear 515b, and by means of the safety ring 515c is free to play in the axial direction. To prevent the tilt of the ca 515 from the axis of rotation of the driving unit, the first bearing 519 is provided between the inertial flange 538 engaged with the drive shaft 503 and the box 515, another bearing 558 supporting the the case is rotatable against the pulley cage 543. Both bearings 519, 558 are arranged to avoid the load tilting moments, within the plane of the pulley RE. According to the thought of the invention, in all the embodiments, other secondary aggregates can be connected in the thrust of the band, so that in this case also the supports benefit from the optimum course of the roll moment. A prestressing of the 555 band takes care of its trouble-free operation. In FIG. 7, an exemplary embodiment for a strip drive 759 is shown schematically. Here a force feeder 761 is attached to the lever 754 which is attached to the mechanism case 715. The force feeder joins the two tension rollers 757a, 757b directly to each other, where the force feeder 761 on both rollers of tension 757a, 757b exerts a tensile force. Between the tension rollers 757a, 757b and the force feeder 761 each time a part of the web 755 runs so that the two web discs or pulleys 762, 721 are connected with the web 755 to the pulley axes arranged 713, 762a in the electric machine or in the drive shaft, the band being left on both sides tensioned against the force of the force feeder 761. In case of need they can be made in the belt drive 659, as well as in any other embodiment of action joints between the drive shaft and the electric machine tree additional secondary aggregates. The embodiment example of a mechanism 809 in FIG. 8 has two different axes 803a, 865 of the drive shaft 803 and the pulley 821 with the distance d. The belt pulley or disk 821 is radially inwardly and present after the web surface 82a an L-shaped flange 82Ib, to receive the planetary mechanism 809a in the disk portion 825c axially molded at the radial height of the shaft. drive 803, as well as a stump 82lb disposed about shaft 865 with an outer gear 82le where the parts are welded together. The toothed wheel 813 is by means of an internal toothing 813a connected in a turning lock with the stump 82id and bolted therewith by means of the screw 813b. The rotatable mounting of the sprocket 813 by means of the bearing 813c and thus of the pulley 821 is carried out in the case 815 that surrounds the sprocket 813 on the peripheral side, furthermore, a seal 830 is provided. The sprocket 813 is engaged with another toothed wheel or gear 866 that compensates for the distance d, and which forms for the planetary mechanism 809a disposed about the axis 803a of the drive shaft 803 the sun wheel, where around this sun wheel 866 the planetary wheels 814 are arranged by means of the shaft 818 on the rod 817 and the box 815, which consists of the parts 815a, 815b formed by means of an internal toothing 816 the hollow wheel. The case 815 is by means of the fixed and axially sealed bearings 819, 836 on the carrier flange engaged and screwed with the drive shaft 803, on the one hand, and on an axially formed projection 866a of the sun wheel 866 which by its part by means of two freewheels 820 arranged on the outer periphery of an L-shaped flange 866b, are intended to increase the torque transmitted, free wheels that are placed on the internal periphery of an axial projection 838a of the carrier flange 838 opposite the drive shaft 803. In addition, it is mounted on the outer periphery of the carrier flange 838 on a second freewheel 822 of three parts, the rod 817, so that the following operating mode of the mechanism 809 occurs: a moment of rotation in the drive shaft 803, then it rotates the axis 803 and rotates the sun wheel 866, after the freewheel 820 which closes in this direction, where the eda libre 822 is over rolled. The torque is transmitted to the gear 813 and the belt pulley 821 to drive the electric machine. Here the pulley shaft 855 rotates about the axis 803a of the drive shaft 803 until the moment of support rotation is counteracted by the tensioned band. Here it should be noted that the distance of the axial displacement between the axes 803a865 is sufficiently large so that with a predated tension of the band in dependence on its frictional forces on the friction surface 82la, the shaft 865 does not slide completely and makes a complete turn about the axis 803a, which at a distance of , greater than 10mm would be excluded with normal conditions. The upper value for the distance d, comes from the structural measures of the 809 mechanism and must not exceed 250mm. If the moment of rotation of the electric machine is driven through the pulley 821 and rotates the mechanism 809 about the axis 803a, then it will continue until reaching the necessary support or stop moment on opposite sides of the belt. Here the moment of rotation of the gear 813 is transmitted to the sun wheel 866 that with the free wheel 820 open, drives the planetary wheels 814 and with the decrease in the number of rotations that occurs the torque is driven on the rod 817 and on the closed freewheel 822 on the carrier flange 838 to the drive shaft 803 to start the drive unit. In FIG. 9, an embodiment of a mechanism 909 with an axial displacement between the axis of the drive shaft 903 and the shaft 965 of the pulley 921 with two pairs of gears 967, 968 and two freewheels is represented schematically. 920, 922 for adjusting the automatic transmission. The first cogwheels or gears 967a, 968a of the gear pairs 967, 968 are disposed fixed to the rotation on the axis of the belt pulley 965, the second gear wheels 967b, 968b are disposed on the freewheels 920, 922 which are opposite each other in reference to the direction of the bearing and placed on the drive shaft 903. The box 915 surrounds the mechanism 909 and is mounted on the shaft 903 by means of the bearings 936a, 936b. In the start-up process, the free wheel 920 is closed and the free wheel 902 is over-rolled, so that a transmission of the number of rotations of the electric machine is carried out slowly. In the operation as a generator, the free wheel 922 is closed and the free running 920 is overturned for the formation of a small transmission. As described with respect to Fig. 8, the box is supported on the band, so that a mounting on the box of the driving unit can disappear. The mechanism 1009 shown in section in Fig. 10, is carried directly by an electric drive-generator machine. For this, the connecting part 1038 in the form of a sleeve 1038 is connected to the shaft 1012 of the electric machine not shown in detail. This connection is made, on the one hand, by the form-closing connection 1003d for the transmission of the moment of rotation and, on the other hand, by means of a screw connection 1003a for axial fixing. The mechanism 1009 has a box 1010, which receives the different elements of the mechanism, especially the hollow wheel 1016, the planetary wheels 1014, the planetary carrier 1017, the sun wheel 1018, as well as different drive or switching elements. The housing 1010 is mounted rotatably with respect to the connecting part 1038 and precisely here by means of a bearing 1019 which includes a ball bearing. The case 1010 has an annular portion 1020 which is formed in the cross-section in the form of an angle and is fixedly connected by means of screws to a second case part 1021. The case part 1020 bears contour 1022 preferably for a transmission agent. endless as especially a toothed band. In the illustrated embodiment, the perfringements 1022 are constructed directly by the housing part 1020.

The planetary mechanism 1009 has sprockets provided with an inclined gear 1014, 1016, 1018. The hollow wheel 1016 is axially displaceable in the box 1010 that receives it. In addition, the hollow wheel 1010 is rotatable with respect to the sun gear or gear 1018. In the illustrated embodiment, the sun gear 1018 is formed directly by the connecting part 1038 formed in the form of a hub. In the connecting part 1038, the ball bearing of the support 1019 is directly received. The part of the box 1020 which forms a pulley is here fixedly connected by means of screw connections 1023 to the planetary carrier 1017. The hollow wheel can be assembled axially 1016 it is connected in drive by means of a ball ramp mechanism 1024 with a ring-shaped component 1025 extending around the shaft 1012. Between the hollow wheel 1016 and the annular component 1025, an energy storage device is axially tensioned. shape of a corrugated spring. The annular component 1025 is rotatably received in the case 1010 - here in the case part 1021 by means of a support 1027. By means of the support 1027 is the annular component 125 fixedly mounted also in axial direction with respect to the 1010. By means of the support 1027, which includes a ball bearing here, axial forces can be captured which, as will be described later, are generated by the ball-ramp mechanism 1024. The annular-shaped part forms a shape-shaped radially inward annular protrusion 1028 carrying a coupling disc 1029. At least the friction zones 1030 of the coupling disc 1029 are displaced in axially limited manner. In the illustrated embodiment, a coupling by means of an axial toothing 1031 has been provided between the coupling disk 1029 and the axial projection 1028. The friction zones 1030 can, however, also be connected to the annular component 1025, by means of an agent of the type of leaf springs in the form of a membrane, a medium that allows the desired axial extension.

The coupling disk 1029 is a constituent part of an aggregate or braking or coupling assembly 1031, which can be constructed, for example, as an electromagnetic brake or coupling. In Fig. 10, an electro magnet is schematically represented and marked with the digit 1032. As already mentioned, the hollow wheel 1016 is axially positionable, so that because of the inclined gear of the mechanism 1009 and depending on the direction of torque transmission, it can be moved axially to the right or to the left. The direction of the axial force component, which acts on the hollow wheel 1O16 is thus dependent on the direction of transmission of moment of rotation which is different in the operation of starting-on or generator. The hollow wheel 1016 is fixed to the rotation with the box 1010 by means of a coupling 1033. In the illustrated exemplary embodiment, the coupling 1033 is constructed as an axial claw coupling, wherein the clamps may have a saw-like conformation in the peripheral direction. By means of the formation of saw teeth of the coupling of the claws 1033 forming the profiles, it is also possible to exert a displacement force on the hollow wheel 1016 depending on the direction of moment of rotation exerted on the hollow wheel 1016. In addition, it can be caused in this manner that the coupling 1033, which in a direction of relative rotation between the box 1010 and the hollow wheel 1016 acts similar to a freewheel, on the contrary, in the other direction of relative rotation between the parts corresponding design elements, a transmission of the moment of rotation through a form closure is presented. With the coupling 1033 closed, the hollow wheel 1016 is at least in a direction of relative rotation with e > 5 relative to the box 1010 or in reference to the planetary carrier 1014 fixedly attached to the rotation or for the drive, whereby the planetary mechanism is in short circuit. With this, there exists between the intermediate shaft 1012 and the box 1010, a transmission ratio i = l. Preferably the mechanism 1009 is constructed in such a way that this transmission ratio i = 1 exists in the operation of the electric machine coupled with the mechanism 1009 by means of the shaft 1012 when it acts as a generator, where in this operating state the coupling will be open 1031. The mechanism 1009 further includes a locking ring 1034, which at least allows some synchronization between the sprocket 1016 and the planetary carrier 1017, before the profiling of the collection 1033 which is carried on the one hand by the hollow wheel 1016 and on the other hand by the planetary carrier 1017, are portable to the grip. A part of the axial force required for closing the coupling 1033 can be applied through the power feeder or the corrugated spring 1026. The inclined teeth of the gear wheels 1014, 1016, 1018 are preferably directed in such a way that in a transmission at the moment of rotation of the drive motor connected with the mechanism 1009 (as especially a combustion machine of a vehicle), produce in the electric machine (this means a degenerating operation of the electric machine connected by means of the shaft 1012 with the mechanism 1009), an additional axial force on the hollow wheel 1016 in a counterclockwise direction, that is in the closing direction of the coupling 1033, whereby the planetary mechanism 1009 is blocked. In this state, the annular component 1025 runs as well as the coupling disk 1029 connected to it, under vacuum. The axial force generated through the ball ramp mechanism 1024 on the component 1025 is captured axially by the support or bearing 1027. By closing the coupling or brake assembly 1031, the annular component 1025 is secured against the rotation, so that a generator operation of the electric machine will exert an axial force through the inclined teeth of the mechanism 1009 on the hollow wheel 1016, on the right. The coupling aggregate 103i and the ramp mechanism 1024 must thereby receive or support a moment which is directed in the direction opposite to the direction in the operation of the electric machine as running. The driving mechanism 1024 is constructed in such a way that it displaces the hollow wheel 1016 during the braking process by means of the coupling aggregate 1031 from the left position against the force of the power feeder 1026 first axially to the right, and then it is placed or held fixed with respect to the construction part 1025. This means that the coupling 1033 is thus free, whereby the transmission function 1009 is presented, because the opening of the aggregate can the wheel 1016, because at the moment of rotation that occurs in the drive of the belt accelerate and thus simultaneously by the effective power feeder axiaimente 1026 moving to the left, so that later at least approximately a synchronization between the number of rotations of the hollow wheel 1016 and the planetary carrier 1017, and then the coupling is closed and with this the function can be bridged of transmission of the mechanism 1009. With this again possesses the mechanism 1009 to the small transmission i = i. The transmission with the released mechanism 1009 can advantageously be in the magnitude of 1.5 to 5, preferably in the magnitude of 2 to 4. The coupling or braking attachment 1031 is advantageously carried through the box 1035 here schematically represented of the generator start-up machine, which has the shaft 1012. The shaft 1012 is preferably connected directly to the rotor of the electric machine or carries this rotor. The embodiment shown in Fig. 11 of a start-generator machine 1100 also has a web pulley 1122 with contours 1122a. Also in this embodiment, the band pulley 1122 forms a constituent part of a box 1110, in which a planetary mechanism 1109a can be received. The planetary mechanism 1109a has a connecting part 1138 which is fixedly connected to the shaft 1112 of the electric machine, similarly to how the part 1038 is fixedly connected to the shaft 1012. The connecting part 1038 constructed as a sleeve carries a wheel 1118 which here is constructed in one piece with the part 1138. The planetary carrier 1117 is likewise constructed in one piece with the band pulley 1122. The hollow wheel 1116 mounted rotatable in the box part 1110 is joined with a coupling disk 1129 which is a constituent part of a coupling attachment 1131, which, depending on the determined operating conditions of the combustion engine of a vehicle linked during operation with the belt pulley 1122, is switchable. In a simple manner, the coupling attachment 1131 may be formed by an electromagnetic coupling or brake, preferably as a brake. The gear or toothing of the mechanism 1109a having at least the hollow wheel 1116, the sun gear 1118 and the planet wheels 1114 are preferably constructed as a linear gear. The web pulley 1122 is mounted rotatably with respect to the connecting part 1138 through a free wheel 1133. The free wheel 1133 essentially assumes the function of the collection 1033 according to Fig. 10. The embodiment according to FIG. 11, it has the advantage that no axial forces are present in the mechanism and it is not necessary according to the ramp mechanism as in the embodiment according to FIG. 10. During the start-up, the coupling 1131, whereby the hollow wheel 1116 is stopped without rotation. By means of the braking of the coupling disc 1129, the greater transmission of the mechanism 1109a is achieved. The mechanism 1109a, is constructed in such a way that in a recessed recessed wheel 1116, the free wheel 1133 effective between the sun wheel 1118 and the carrier 1117, it is about rolling in the operation of the electric machine connected with the shaft 1112 as an initiator for the internal combustion machine. As soon as the internal combustion engine is turned on and has a corresponding number of rotations, the direction of transmission of the torque is reversed. This means that, then, the electric machine connected to the shaft 1112 will be driven by the internal combustion engine. If in this state the hollow wheel 1116 or the coupling disk 1129 is still held fixed against rotation, the largest transmission of the planetary mechanism 1109a is presented for operation as a generator. If the hollow wheel 1116 or the coupling disk 1129 is free then they can practically rotate freely, and in the generator operation no drive load of the belt pulley 1122 can be transmitted to the shaft 1112, by means of the gears or gearwheels of the planetary mechanism 1109a, whereupon the freewheel 1133 is locked and the band pulley 1122 rotates synchronously with the shaft 1112. With the hollow wheel 1116 being braked, the shaft 1112 rotates in generator operation more rapidly than the construction part 1122, so that then the freewheeling function of the freewheel 1133 is effective. The mechanism 1200 shown in Figs. 12 and 13 for a start-up machine -electric generator is similarly connected, as described in dependence with Figs. 10 and 11 with shaft 1212 of the rotor of the electric machine. The band pulley 1222 is connected to the planetary carrier 1217 and the shaft 1212 * -v with the sun gear or gear 1218. The planetary mechanism encompassing the planetary wheels 1214, the planetary carrier 1217 and the sun wheel 1218 has an inclined gear through which the hollow wheel 1216 in a corresponding torque transmission is axially displaceable to switch or connect the different stages of the mechanism 1200 depending on the existing direction of transmission of the moment of rotation. The hollow wheel 1216 is axially positionable with respect to a component 1238 which can be fixed against rotation by means of a brake 1231 which operates in a similar manner to the brake 1031. The gears of the planetary trains 1214, 1216, 1218 have gears inclined The angle of inclination is selected in such a way that the hollow wheel 1216 can be displaced by the forces generated in the areas of the teeth in the axial direction. If the shaft 1212 moves the hollow wheel 1218 and the crankshaft of the internal combustion machine is driven by the planetary carrier 1217, then the hollow wheel 1216 is pushed to the left by the inclined gear (Fig. 12) and continuously presses on the constructive part 1238 that is outside. The moment of support that is produced is transmitted in the contact surfaces by the form 1233 closing, for example through a saw-like gear, claws, etc., and / or in a flow of force (friction). Since the hollow wheel 1216 is kept fixed because in this operating state the construction part 1238 is kept fixed by the rotation by the brake 1231, this arrangement produces the largest transmission at a slow speed that allows the start-up of the machine of internal combustion through the discs or pulleys 1222. If the discs 1222 or the planetary carriers 1217 are driven by the crankshaft, and with this the axes 1212 by the sun wheel 1218, then the direction of force in the hollow wheel is reversed 1216. In this way, it is pushed to the right and pressed against the planetary carrier 1217. The connection between the hollow wheel 1216 and the stopped constructive part 1238 is interrupted and another connection is produced by closing force and / or form 1235 ( see Fig. 13) between the planetary carrier 1217 and the hollow wheel 1216. The planetary train is blocked in this way and the sun wheel 1218, the planetary carrier 1217, the planetary gears 1214 and the wheel. hollow 1216 rotate together with the shaft 1212 as a rigid unit. This produces a direct transmission of one for the operation as a generator. The mechanism 1200 further possesses a centrifugal force coupling 1236 with force / J centrifugal elements 1237, which radially inwardly are pushed through a feeder or energy storage 1238. Through the centrifugal force coupling 1236 the mechanism 1200 can to be blocked depending on the number of revolutions of the pulley or band disk 1222 or the number of impulse revolutions of the internal combustion engine in the switching state shown in Fig. 13. The mechanism 1200 shown in Figs. 12 and 13, has a similar work form as well as an operation to the mechanism 4-09 according to Fig. 5, where however the conformation of Fig. 12 and 13 does not present according to buffer or limiter, For many cases of application, it may, however, also be convenient in this embodiment to provide a shock absorber and / or a limiter. It is particularly suitable, however, if, in combination, an electric generator run, which carries a mechanism 1200, the damper and if necessary the still existing limiter is arranged or arranged in the crankshaft of the combustion machine, which drives to the mechanism 1200. The damper or limiter may, as is known per se, be integrated in the belt pulley provided by the side of the internal combustion engine. By the application of the constructions of the mechanism according to Figs. 10 to 13, internal combustion engines can also be produced with a high start-up time. By means of a suitable arrangement of the mechanism, greater transmissions in the band operation can be guaranteed and precisely in the sense of a multiplication of the number of revolutions of the electric machine, so that to produce the necessary torque for the combustion machine the required number of revolutions can be set internally. For operation as a generator, a transmission is necessary and precisely in the sense of one of multiplication of the number of revolutions transmitted to the shaft of the electric machine. Also this lower number of revolutions for the rotor of the electric machine, can be obtained by the conformations according to the invention and the arrangements of a mechanism in the electric generating set-up machine. The arrangement of the mechanism in the generator-gear machine also has the advantage that in this way the mechanism can have an essentially smaller dimension. In Fig. 14, another arrangement possibility of an electric generator-running machine 1308 is shown within a drive train 1301. The drive train 1301 has a driving unit 1302 for example / D a combustion engine, whose shaft of output or power take-off 1303, is coupled by a coupling 1304 with a mass of inertia 1310. The rotatable mounted inertial mass 1310 is unible by a second assembly 1304 with the input shaft 1305 of a power take-off unit, output or armature shaft 1306, for example a mechanism. With reference to the possible shaping of an oscillating or inertia wheel of this type 1310 and of the couplings 1304 and 1304a, we refer for example to DE-OS 2917 138, DÉOS 2931,513 and ДДOS 2748,697. The electric machine 1308 is connected to the drive by a belt or chain or, if necessary, by a gear connection with the flywheel 1310. Advantageously, a transmission mechanism 1309 can be connected to the electric machine 1308, where this mechanism 1309 is arranged coaxiaiently with the rotor shaft of the electric machine 1308. The mechanism 1309 can be constructed according to the mechanism already described, especially presenting a conformation according to Figs. 2, 3, 10, 11, 12 and 13. Fig. 15 shows a drive train 1401, similar to the embodiment of the drive train i '' of Fig. 1, in which the mechanism of the wrapping agent for The 1406 speed change mechanism has a continuously adjustable transmission (CVT). The transmission variation of the mechanism 1406 is carried out - in a manner known per se by means of a pair of conical discs 1450 and 1451, arranged on the input shaft of the mechanism 1454 and the output shaft of the mechanism 1453 with each time two conical discs 1450a, 1450b, 1451a, 1451b, where axially between the conical discs 1450a, 1450b, 1451a, 1451b, the wrapping means 1452 is taken in a friction closure, and the conical discs of the pairs of conical discs are axially displaceable one against the other by means of hydraulic, mechanical and / or electrical displacement agents, and thus the desired transmission between the internal combustion engine 1402 and the armature output shaft can be adjusted by means of an adjustable running diameter of the surrounding medium. 1453 of the mechanism 1406. In the force flow between the internal combustion engine 1402 and the mechanism 1406, the electric machine 1408 is disposed axially around the input shaft of the mechanism 1454, where it is up to the deflection caused by the termination of the axial extension of the crankshaft 1402a of the combustion machine 1402, and between both axes 1402a and 1454 a running coupling 1404. Preferably for the purpose pursued is the idle coupling / / 1404 arranged in force flow between the electric machine 1408 and the mechanism 1406 where this can be disposed outside the mechanism 1406 in the coupling hood as a dry coupling or placed in the mechanism case can also be performed as a wet coupling. Coupling 1404 may be equipped for damping torsional oscillations with a torsion damper - not shown here, or as part of a split flywheel, where rotor 1408a of electric machine 1408 may be constructed as part of primary oscillating mass and coupling 1404 as part of secondary oscillating mass, where the relative rotation of the two parts 1408a, 1404 against the direction of rotation -as it is known per se- produces a damping device. As necessary, a mechanism 1409 radially inward of the outer periphery of the rotor, which is adjusted depending on the operating states of the driving installation 1401 to the rotor 1408a and the crankshaft 1402, is provided as necessary. the proper transmission automatically. The operating states are at least the start-up process of the combustion machine 1402 in which the coupling 1404 is preferably open -in the closed coupling 1404 and the rolling vehicle can for energy saving reasons start with the machine of combustion 1402 by a controlled closure of coupling 1404 with or without transmission of electric machine 1408, and mechanism 1409 transforming the number of rotations of electric machine 1408 to slower, and in generator operation in which the number of rotations of electric machine 1408 is not transformed or transformed to speed. In addition there is a way of operation, in which both engines, the internal combustion or explosion machine 1402 and the electric machine 1408 -which drive the vehicle in which an impulse initiation and / or recovery of the aforementioned one is possible, but only if the combustion engine 1402 has controllable combustion valves 1402b for a purpose pursued or electrically aimed, for example piezoelectric which are controllable independently of their working strokes, so that the moment of thrust attached to the compressive work of The internal combustion engine can at least partially be eliminated. In the driving gear first with the valves 1402b open, the combustion machine is accelerated by the electric machine 1408, then the valves and 1402b are closed, and the work is continued. In the recovery, the electric machine 1408 is used for the delay of the vehicle where the moment of delay is formed by the generation of electric power that is conducted to an electric aimacenador not shown. The valves 1402b of the combustion machine are thus prepared for the reduction of the pushing or sliding moment of the combustion engine by opening, so that, if necessary, by closing the valves, especially with an unloaded electric machine 1408, the vehicle can cope additionally. It is understood that these control and regulation processes can be controlled by a calculating machine -not shown- and that in addition, the fuel supply in those operating states can be adjusted accordingly to decrease the fuel expense, when for example some cylinders whose compression through the opening of the valves 1402b are also open in the working stroke and thus do not produce according to expansion work, nor will they be provided with fuel. Figs. 16 and 17 show exemplary embodiments of the drive trains 1501, 1601 similar to embodiment 1401 in FIG. 15, which in difference to the drive train 1401 presents another shaped coupling arrangement 1504, 1604, and an additional coupling 1504a, 1604a, in the force flow between the electric machine 1508 and 1608 and the drive wheels 1560, 1660, where the electric machine 1508 of the drive train 1501 is arranged concentrically around the input shaft of the mechanism 1554 and the electric machine 1608 is parallel to the input shaft of the mechanism 1654 and joined in a force closure with this, by means of an active connection 1607. The coupling 1504, 1604 is arranged in force flow between the driving unit 1502, 1602 and the electrical machines 1508, 1608 so that an isolation of the combustion machine 1502, 1602 from the rest of the drive train is possible and with this it can be recovered independently Furthermore, in a closed coupling 1504, 1604 and open coupling 1504a, 1604a, a direct running is possible, as well as in open coupling and open assembly 1504a, 1604a, with a running of 1502, 1602a. pulse, where after the acceleration of the electric machine 1508, 1608, or its masses provided in the rotor 1508a, 1608a the coupling is closed and the combustion machine 1502, 1602 is started. In order to stabilize the number of revolutions of the the combustion machine 1502, 1602 especially in a vacuum or in neutral stroke with the coupling - w?. 81 open 1504, 1604, it may be advantageous to provide on the crankshaft 1502a, 1602a an additional oscillating mass 1502c, 1602c, where in some cases it may be advantageous to immobilize the drive unit 1502, 1602 when opening the coupling 1504, 1604, where the drive unit can start up automatically again, after the closure of the coupling 1504, 1604. The oscillating or inertial mass of the rotor 1508a, 1608a can serve during the recovery process additionally as a mechanical energy storage. This has the advantage in the use of a continuously adjustable mechanism 1406, 1506, 1606, according to Figs. 15, 17, which during the recovery of the mechanism can be adjusted a transmission of the wheels 1560, 1660 to the rotor 1508a, 1608a in speed (Underdrive), so that a high delay can be caused with a rapid acceleration of the rotor, so that this together or alternatively to the generation of electrical energy can also store mechanical energy in the form of rotation. In a subsequent acceleration of the vehicle this energy can be transmitted by means of the corresponding adjustment of the transmission of the mechanism 1406, 1506, 1606 to the wheels. The mechanical recovery will be energetically more favorable due to the disappearance of conversion losses. It is understood that the coupling 1504a, 1604b can also be arranged in force flow between the electrical machine 1608 and the mechanism 1506, 1605, the couplings 1504, 1604, 1504a, 1604a, can be constructed dry or wet and integrated into the housing of the mechanism or in the coupling bell of the mechanism 1506, 1606. In addition, the mechanism 1406, 1506, 1606, shown in Figs. 15-17 as CVT can also be replaced by another mechanism that is desired such as for example an automatic cover mechanism, a mechanism or gearbox manual switching or the like. In Fig. 18, an exemplary embodiment of a mechanism 1609 is shown which is similar to the mechanism 409 of Fig. 5. While in the mechanism 401, however, a locking mechanism or latch controlled by the centrifugal force ensures the adjustment of the transmission to io fast in an active one, this is electric driving machine for example, in a Boost operation, by means of centrifugal force, it is closed in the present embodiment, each of the two stages of transmission by an installation controllable closure from the outside 1680. The closing or latching installation 1680 is composed of an electromagnet 1681 controllable from the outside and of units distributed in the periphery each consisting of a punch 1682, a wedge 1683 and a closing agent as sphere 1685, where the electromagnetic magnet 1681 pushes the wedge 1683 axially against the effect of an axially active energy storage 1684, which hangs on the inner periphery of an outlet. axial member 1603f of the sun wheel 1613. The closing spheres 1685 fix the axial position of the hollow wheel 1616 when they form an axially shaped closure between the hollow wheel 1616 and the axial projection I6l3f. For this they are displaced by the wedge 1633 during its actuation by the electromagnets 1681 from the projection or stop 1613 radially in the grooves 1686a, 1686b, coordinated to the two transmission stages where the wedge 1683 for this has a corresponding ramp geometry 1683a. The backward movement of the spheres 1685 radially inwards is carried out by electromagnets 1681 traversed by an opposite current and which in this way displaces the wedge against the axial effect of the energy storage 1684, and the profile of the grooves 1686a, or 1686b if appropriate, drives the spheres 1685 radially inward in the sunken profile in this position 1683a of the wedge 1683. With the aid of the closing device 1680 in the electric machine which acts by rotation on the sun wheel 1613 (which does not it is shown) by the wedge band surface 1628 can be blocked or both transmission states established, where the electrical machine acts in synchronization with the switching of the mechanism. In the state shown in Fig. 18, in which by means of the gear 1616c, the wheel 1616 is engaged in the box and with this results a slow transmission, it can if the combustion machine is turned on an inversion of the moment of rotation and the electric machine drives the transmission not varying by an axial displacement of the hollow wheel 1616 through the inclined gear 1616a to the fast, position, the closing spheres 1685 forming with the slots 1686a of the hollow wheel 1616 an axially shaped closure, will prevent this, firstly until after the opposite current in the electromagnets 1681 the wedges 1683 free the axial movement of the wheel hollow 1616 when the spheres 1685 are displaced radially inwardly. The hollow wheel 1616 moves axially to the position with lines 1616 'and the direct transmission of the mechanism comes into action. This position can now be re-closed when the closing or latching spheres 1685 by the axial displacement of the wedges 1683 against the effect of the energy canceller 1684 and causes the ramps 1683a to move to the slots 1686b. In an inversion of the direction of the moment of rotation, for example in a Booster operation or single operation It is from the vehicle by the electric machine the high transmission stage is maintained. The embodiment example of a mechanism 1709 shown in Fig. 9 is similar to the mechanism 409 of Fig. 5, and is optimally especially in reference to the degree of efficiency by a reduction in the loss of grease or oil by narrow recesses. For this, the case 1615 fixed by means of retainer indicated 1702 in the housing or housing (not shown) of the drive unit is optimal in terms of its construction space and its rotating parts avoiding neighboring narrow notches, against surfaces that rotate against each other. For this a variation of the principle of operation is necessary - in comparison with the mechanism 409 of Fig. 5. The inclined direction of the gear 1715a between the planetary train 1714 and the hollow wheel 1714 is reversed, so that the hollow wheel moves to the switching of the mechanism stage in slow motion axially in the direction of the retainer 1702 and form with the housing 1715 by means of 1716c a form closure, whereby the torque of the electric machine through the belt pulley 1743 , which is connected to the sun wheel 1713 coming from the planetary train 1714 to the rod 1717 and from there to the drive shaft 1703 connected to the rod 1717, arriving at the combustion machine, for example for its start-up. An inversion of the moment of rotation causes an axial displacement due to the inclined gear 1716a of the hollow wheel 1716 moving away from the drive shaft 1702, where the shape lock of the hollow wheel 1716 is removed from the case 1715, while through the gear 1717a, the hollow wheel is joined to the rod 1717 through a flange 1717b running radially outwardly, which at its outer periphery has an axial projection 1717c in whose passage to the radial flange 1717, the damper 1739 and its end free of the limiter 1740 are taken in its internal periphery. Therefore, the damper 1739 is no longer in force flow between the planetary train and the drive shaft as in Fig. 5, but between the rod 1717 and the hollow wheel 1716, and only in the transmission to fast is effective and thus during extreme oscillation situations during the start-up of the combustion engine, it is uncoupled for which it can be mounted more weakly. To close or establish the hollow wheel 1716 in the high transmission stage, the centrifugal force segments 1752 which grip radially outwards in dependence on the centrifugal force and are distributed in the periphery and received in openings I7i6e, made in the axial projection, serve 17d, segments which during the active to fast transmission stage fit into widened shoulders 1752 of the shock absorber 1739 against the radial effect of the energy absorber 1752b, which are correspondingly arranged radially at the periphery, and thus with an inversion of the torque with High rotation numbers for example in a Boost process fix the hollow wheel in this transmission stage. As the number of rotations sinks, it causes the radiatively effective energy canceller 1752b, a loosening of the centrifugal force segments 1752, and thereby the removal of the closing of the hollow wheel 1716. With this arrangement, mechanism 1709 is presented in FIG. the essentials without thin recesses between the fixed parts and the rotatable parts and the border surfaces, with which the lubrication means 1785 applied in space 1785 has less cutting losses and with this the efficiency degree of mechanism 1709 is raised. Fig. 20 shows a section of a drive train in which the mechanism 1809 is disposed radially inward of the electric machine 1808 and directly on the drive shaft, as the crankshaft 1803 of the combustion machine 1802 only partially shown. Here is the mechanism 1809 placed on the side of the original belt pulley of the crankshaft 1803 on the side opposite the mechanism (not shown) for the operation of the vehicle. The usual secondary power drive as for example, auxiliary steering pump, air conditioner and the like, as well as the valves driving, can be performed in another way, for example electrically. The generator unit set-up 18, consisting of the electric machine 1808 and the mechanism 1809 is placed completely mounted on the casing 1802a of the driving unit 1802. For this the electric machine 1808 can be referenced to a spacing 1808a between the rotor 1808 and the stator 1808c is already fitted, where for this the mounting adapter 1802b can take a position equal to the box 1815 and the stator 1808c, and the rod 1817 of the mechanism 1809 is centered, and by means of an axial profile (here in shape) at least one bolt 1803a axially directed), forms a form closure with the drive shaft 1803, then the mechanism 1809 fixed to the rotation and fixedly fixed to the rotation by means of the fixing agent 1802c with the case 1802a of the drive unit 1802, where the rod 1817 as the input part of the mechanism 1809 from the drive unit 1802 screws with a central screw 1803b to the drive shaft 1803 and the opening Central screw 1813a is lockable on sun wheel 1813 for gripping through the mounting tool with a closing hood 1813b. In the example shown, there is the mounting adapter 1802b formed by a molded part of the sheet which on its outer periphery by means of tongues 1802 axially established and distributed on the periphery take the stator 1808c by fixing it axially and in rotation, where it can be screwed , welded, or riveted with the I802d tabs. In the area of the inner periphery of the molded part of sheet 1802b, there is an axial projection 1802e for the taking and support of the box 1815 provided with bolts I802f directed radially out of the projection and axially for the union in rotation closing of the housing or housing of the mechanism 1815 with the casing 1802a of the driving unit 1802, which grip axially in correspondingly shaped recesses 1817a, I802g. The molded sheet portion 1802a is axially secured in the housing 1802a of the driver unit 1802 by means of a locking agent distributed on the periphery 1802c, such as screws or hollow bolts. The mechanism 1809 disposed radially inside the rotor, operates in a similar manner as shown in the embodiment samples 409, 1609, 1709 in Figs. 5, 18, 19 with a hollow wheel 1816 displaceable axially in dependence of the direction of the moment of rotation, which is displaced axially by means of an inclined gear 1816a between this and the planetary train 1814 and with this commuted by means of the gears 1815a, 1817a, of the two transmission stages, when by means of the gear 1815a, the hollow wheel 1816 is joined in a rotation or rotation closure to the case 1815, and with this a planetary train or seat 1814 is guided through the moment of rotation from the rotor 1808b, fed to the sun wheel 1813 through the flange portion 1813c, to the rod 1817, which thereby starts the drive unit 1802 by rotating the drive shaft 1803 through of a slow transmission. In a change of direction of moment of rotation, for example, when the drive unit 1802 is started and start operation as a generator, the hollow wheel 1861 experiences an axial force component through the inclined gear component 1816a which in its extension axial and a separation of the form closure of the gear 1815 with the housing 1815 attached to the previous extension forms a form closure by means of the gear 1817a with the input part 1848a of the torsional oscillation damper 1848, whose outlet part 1848b is attached fixed to the rotation with the rotor 1808b as well as with the sun wheel 1813, where the input portion 1848a and the output portion 1848b are rotatable relatively against each other against the effect of the energy canceller disposed at the periphery 1848c, so that with the intermediate switching of the shock absorber 1848, the rotor 1808b the sun wheel 1813 is directly connected to the rod 1817 and thus to the drive shaft 1803 and is switched to the second transmission stage with a transmission 1: 1. To facilitate the switching or speed change process - as in the other mechanisms 409, 1609, 1709 with equally advantageously axially displaceable hollow wheel - the hollow wheel 1816 brakes against the rod 1817, so that in a hollow wheel that rotates slightly , the combs of the gears of the planetary train 1814 with the hollow wheel 1816 without axial displacement of the hollow wheel 1816 is avoided. For this purpose in this embodiment, the ring gear 1816b of the hollow wheel 1816 with spring segments 1816c distributed on the periphery and preferably 3 is axially tensioned, and the tabs I8l6d radially directed centrally inward, grip on a turn lock in the radially inwardly opening openings 1817c, and thereby increase in a relative movement of the hollow wheel 1816 with respect to the rod 1817 in the peripheral direction, a moment of friction therebetween also increases the axial force components. In addition, the spring elements 1816c in conjunction with the openings 1817c serve as synchronization of the gear 1817a. This function is shown in more detail in Fig. 21, which shows a cut of the ring gear 1816b of the hollow wheel 1816 (Fig. 20), in which the spring grip 1816c has been carried holding around its inner periphery and its attached, and by means of established tabs I8i6h it remains in frictional contact with that. The radially-inwardly-turned tabs I8l6d grip in the recess 1817c which has been placed on the outer periphery of the rod 1817. The formation of the recess 1817c is carried out in such a way that the tongue I8i6d and with this the ring gear 1816b with the hollow wheel 1816 is displaceable in a first section 1817c1 with respect to the rod 1817 up to a stop 1817C '. This corresponds to the axial displacement of the hollow wheel 1816 in a reversal of moment of rotation from slow to fast with a separation of the closing form between the carrier 1815 fixed in place and the hollow wheel 1816. The stop 1817c '' separates the movement of the hollow wheel 1816 prior to the formation of the shape lock of the gear 1817a between the hollow wheel 1816 and the output portion of the shock absorber 1848a (Fig. 20), until the speed of difference between the ring gear 1816a and the rod 1817 becomes almost nil, so that tongue 183d due to a rod 1817 that rotates slightly faster in the peripheral direction in the second section 1817c '' 'of opening 1817c is moved and then by means of the axial force component of the inclined gear 1816a, the tongue I8l6d and with this the hollow wheel 1816 can be displaced more axially and with a roughly equal number of rotations of the two parts 1816, 1848a a synchronized locking of the gear 1817a can be formed. A renewed variation of the direction of the moment of rotation causes, with respect to the movement of the tongue 18l6d in the opening 1817c a reverse stroke, this however has no importance for the movement of the two parts 1848b, 1816, since in this direction it must not be done according to synchronization work. A synchronization can also be provided for the gear 1815a, but it remains below in the embodiment shown in FIG. 20, since the switching in this transmission stage as a rule takes place with a very small number of rotations. The closure opposite the latch of the rapid transmission stage of the embodiment example shown in FIG. 20 is realized by means of centrifugal force segments 1852 (preferably 3) distributed on the periphery, which penetrate radially into the hollow wheel 1816, and by means of radial outward openings provided in the hollow wheel under the action of the centrifugal force in a radial manner until by a stop not shown exactly they are radially deviated and form when the gear 1817 is closed with the hollow wheel 1816 with ios. free ends of a projection 1848d axially placed in the damper 1848 an axially shaped closure and thereby stop the hollow wheel 1816 in a change of the moment of rotation direction against the force component caused by the inclined gear 1816a, in the position to form the rapid transmission stage, until the number of rotations decreases and in the centrifugal force segments placed radially against the centrifugal force an energy storage that is not accurately represented (compare 1752b in Fig. 19) , the segments of centrifugal force 1852 recede slightly in radius, leaving the hollow wheel 1816 free in the axial direction, so that the can perform the transmission to slow. It is understood that the bolt or bolt can also be realized, for example, by means of a bolt device 1680 in FIG. 18. The arrangement and shaping of the individual parts for the generating unit - set in motion 1801, can be seen from the Fig. 20, whose diameter is essentially given by the electric machine 1808 and its loading requirements. Radially inside the rotor 1808b, the mechanism 1809 is arranged as a peripheral or circular gear mechanism, which however can also be configured as a stationary or friction wheel mechanism, where in both cases the switching of the mechanism steps that can be performed electromagnetically, hydraulically, pneumatically or similarly they can also be made from outside, for example by the coupling drive and / or brakes installed, possibly with a corresponding arrangement of vacuum or free wheels needed. The structure of the present embodiment seeks a use of the peripheral mechanism 1809 in such a way that the rod 1817 is connected in a force closure with the drive shaft as the crankshaft 1803 and the sun wheel 1813 with the rotor 1808b, while the hollow wheel 1816 forms a form closure with the case 1815 or with the sun wheel 1813, under an intermediate commutation of the shock absorber 1848. It is understood that the peripheral mechanism can also be arranged in other variations for the formation of at least two stages of transmission between the drive shaft 1816 and the rotor 1808b. In the exemplary embodiment shown, the rod 1817 is constructed as a radial hub of several stages where axially thereon between the intake on the drive shaft 1803 and the planetary train 1814, which preferably contains three planetary wheels, being essentially integrated in the diameter of the rod 1816, the assembly of the box 1815 being carried out by means of a bearing 1836 which can also be a double support or rider to reduce the falling movements of the two parts mounted one with respect to the other 1817, 1815. In this embodiment, the housing 1815 fulfills the function of a fixed carrier in place rather than a box or housing function, since the volume displaced by the mechanism 1809 essentially by the flange part 1813c connected to the wheel sun 1813 with the axial projection constructed and with the flange portion 1813 having bolted on the front side the rotor carrier I8l3d and with this flange portion 1813e on its other end joined, for example welded, having an L-shaped cross-section, part of flange that with its axially directed branch 1813 is mounted on the carrier 1815, forming a chamber 1885 closed at least partially filled with lubricating agent, with the which limits. In addition, the chamber 1885 is sealed radially outwardly between the flange portion 183e and the carrier 1815 by means of the sealing 1890 Q7 as well as between the rod 1817 and the carrier 1815 by means of sealing 1891. The carrier 1815 as well as the wheel hollow 1816 are advantageously constructed as molded parts of sheet, wherein the hollow wheel 1816 takes on an annular surface 1816c provided on its internal periphery in the inclined gear toothed crown I8l6f, which is joined in a force closure, for example by stressing. The provided means 1848, 1839 for decreasing the rotational oscillations are essentially arranged at the outer periphery of the mechanism 1809 directly radially inside the rotor 1808b, where the limiter 1839 with the limiting mass 1839a by means of an energy storage 1839b acting in the peripheral direction against the effect, with the flange portion 1739b attached to the limiting mass 1838a by means of alternating planetary wheel shafts in the periphery I8i4d and the fitting bolts I8i4e is joined with the shaft 1817 In this way, the limiter is effective in the entire working area of the mechanism 1809 in both stages of speed or mechanism. The arrangement of the restrictor can be provided in an exemplary embodiment not shown exactly at the other end of the drive shaft 1803. The shock absorber 1848 is only switched to the fast transmission when the gear 1817a is closed and is driven through a friction direction 1840 effective through the inlet portion 1848a, and the flange portion 1813c joined with the sun wheel 1813, consisting of the friction disk 1840a and the axially effective energy storage that axially tension the friction disk 1840a, against the flange 1813. The damper 1848 can by means of the mass of inertia of the rotor 1808b and of another mass eventually disposed to the energy storage 1848c in force flow, for example, by placing it on the other end of the drive shaft 1803, so as to result in an oscillating or inertial effect of two masses with a number of rotations of decreased resonance less than the number The start-up rotations, where a particularly effective damping of the torsional oscillations which are applied first from the drive unit 1802 on the drive train or rope, can take place. An optimal state of the inertial masses can take place from this point of view and from the objective of keeping the total oscillating mass to a minimum, where the mass of the rotor also represents a mass of inertia on the drive side, and with this properly inertial wheel can be made small on the side of the mechanism and therefore in this place can be saved constructive space. For example, it is possible in a switching mechanism to limit the size of the oscillating inertia wheel to the coupling pressure plate, whereby more construction space is left free for other systems, for example for automatic actuators of the assembly and / or of the mechanism. In addition, it can be advantageous to use the electric machine 1808 as an "electric oscillating mass", when it is switched, for example, with a slow number of rotations of the driving unit 1802 and, among other things, also to dampen, for example, torsional oscillations by switching Fig. 2 shows schematically an embodiment of a drive train 2001 with a combustion engine 2002, a mechanism 2006 that is realized as a variable wrapper mechanism (CVT), and a 2008 electric machine integrated in the 2006 mechanism in reference to the flow of forces, where the electrical machine referring to its arrangement in the 2006 mechanism or outside the mechanism box 2006a, can be arranged and performed the force transmission 2009 by means of of a band, mechanism of gears or by a direct intake of the electric machine 2008 in the 2005 primary shaft, by means of a direct connection of the armor 2008b in the primary shaft 2005. The active union 2009 can be a self-connecting mechanism or also a fixed transmission. In the example shown, there is the 2002 combustion engine 2002 by means of the crankshaft 2002a which can be subsequently fitted to a torsional oscillation damper 2039 connected to the input shaft of the mechanism 2005a. The input shaft of mechanism 2005a is unible with the primary shaft 2005 by means of a coupling 2004. The primary shaft 2005 takes fixed rotation in the first disk drive 2050 of the enclosing mechanism 2006, which by means of the enclosing agent 2052 is unible in a force lock fixed to the rotation with the second disk train 2051 received in the secondary shaft 2053. The function of a CVT, is in itself known and for example explained in detail in DE 195.44644. The secondary shaft 2053 is uncoupled from the differential 2059 and from the following driving means 2060 by a second coupling 2057. The couplings 2004, 2057 may be friction couplings preferably lamellar assemblies running in an oil bath. In the train or drive rope 2001, a reversing installation is also provided which is not shown. In the drive train 2001 of Fig. 22, the electric machine 2008 is provided at the end of the input shaft of mechanism 2005 opposite the combustion machine 2002. This arrangement is especially advantageous for arrangements with a front or longitudinal transverse installation front of the 2002 combustion machine without Cardano tree, to the rear wheels. For this purpose, the input shaft of the mechanism 2005 can be extended and by means of a watertight sealing ring sealed from the case 1006a. Then the electric machine 2008 is taken either directly coaxially in the input shaft of the 2005 mechanism where the stator is preferably fixed to the rotation with the box 2006a and the rotor is fixed with the input shaft of the 2005 mechanism, as shows axially parallel with intermediate switching of a transmission agent, for example of a front wheel mechanism or of a wrapping agent mechanism 2009, whose discs 2009a, 2009b drive the wrapping agent by different running diameters, and with this can adjusting a variable transmission where this adjustment can be made from outside, for example by means of a control apparatus or automatically for example, by means of centrifugal force. The use of an intermediate mechanism 2009 that can also be provided under a corresponding adjustment, for example radially inside the rotor in a force closing between the rotor and the input shaft of the 2005 mechanism, in a coaxially arranged electric machine 2008, allows an adjustment of the number of rotations of the electric machine 2008 to the area of the number of rotations of the input tree of the 2005 mechanism, where especially the constructive sizes thus reduced can lead to cost and weight savings.

Fig. 23 schematically shows an exemplary embodiment of a drive train or rope 2101, which is identical to the drive rope 2001 of Fig. 22, only in the following differences to be described. The electric machine 2108 is arranged parallel to the axis as shown or axial between the stock 2104 and the disk wheel 2150 coaxially. Here the electric machine 2108 can be arranged with a parallel arrangement to the shaft inside or outside the mechanism case (not shown), where the electric machine 2108 in an arrangement within the mechanism 2109 can be encapsulated against the mechanism oil. It is understood that an encapsulation can be advantageous for all electrical machines integrated according to the invention in the mechanism 2109. A wiring of the electric magneto can be made in a cable tree provided for the control of the mechanism 2109, where a cutting position For example, a common socket joint can be advantageous for the care of the gear components and the electrical machine. Lae Figs. 24a to 24c show, a counter position of the moment course in the time of the change of thrust operation of the vehicle delaying the traction operation to a renewed acceleration. Fig. 24a, gives the moment of rotation m course, depending on the time t, for a vehicle without recovery, in which the combustion machine by means of its moment of push M (engine brake) delays in the vehicle , in point 1 a load requirement is introduced by the driver, for example by means of a gas pedal actuation, and the combustion machine changes approximately without delay to the traction operation until the number of rotations increases at the point II, and the vehicle can be moved along the full load characteristic line III. Fig. 24b shows the pushing / pulling behavior of a vehicle with a method for recovery according to the state of the art. The dependence of the moment M, depending on the time t, for the principle of representation is given by a brake moment M (rek), which is used by the electric machine for the storage of electrical energy in the driving rope, for economic reasons here the combustion machine is separated. In a power requirement by the driver, the combustion machine at the point, start. This takes place using the excess kinetic energy of the vehicle in an operation of the electric machine in the generator operation, which additionally needs a moment M (gene). Here the vehicle is produced in the time interval between the point Ia, Ib firstly a recoil, this means that the vehicle is delayed rather than accelerated and not performed according to spontaneous moment increase until the combustion engine is set underway at point Ib, and in the time course until point II a moment is installed by the increase in the number of rotations and in zone III it is driven or operated with full load, such behavior is contrary to the moment course of a vehicle according to Fig. 24a, of large number of drivers who consider it uncomfortable, and will feel intolerable as regards a safe movement of the vehicle. A solution to this problem io shows a method for controlling the electric machine in Fig. 24a. Starting from the brake moment (M) (rek) in which the electric machine brakes the vehicle with current generation at the moment (M rek) the electric machine immediately with a power requirement by the driver at the point is commuted to the drive mode and form before the start-up of the combustion machine a moment M (E) for the momentum of the vehicle. The combustion engine is started between the points la, Ib, where the kinetic energy of the vehicle and the moment M (E) of the machine can be applied for the partial start-up in a faulty or closed gear coupling. electrical or existing a coupling of march, this to avoid a backward movement for a moment opens or works pushing and the electric machine starts the combustion machine alone.

After an example of realization -as shown in the diagram of Fig. 24c -establishes the electric machine immediately after the driver's power requirement, the moment M (E) and supports the drive of the vehicle and the start-up of the combustion machine. At point Ib, the combustion engine is started and, by increasing the number of rotations, it establishes a moment M (BKM) which, in point II, passes to curve III of full load. The regulation of the electric machine is now carried out in such a way that the sum of both moments M (E) and M (MKM) from the moment of power demand until the moment curve M (BKM) in the curve III of full load at point III produces a smooth transition for example without high velocity gradient and / or step gradient of speed nodes. This is done in such a way that the electric machine at the beginning of the power requirement can preferably reach the point that remains before the start-up of the combustion machine at least at the moment of continuous rotation or a little. before accelerating on the moment of continuous rotation, and after the point it again with a decreasing number of rotations, this is the moment M (E) to work where the null step, and with this the step in the generator operation with the tap For the moment, M (gene), for example, is made earlier than point II, in which the combustion machine reaches the full load zone III, it is understood that the electric machine in this phase can also be used exclusively for damping the recoil of the combustion machine, without transmitting additional moment to the driving agent. For this, the electric machine can depend on the mechanism transmission, slow down the number of rotations of the combustion machine in generator operation or accelerate in the drive mode. The applications with the following act numbers are taken completely in the present application: DE 198 12 417; DE 198 38 036; DE 198 33 784; DE 199 25 332 and DE 199 18 787. The claims filed with the application are formulation proposals without prejudice to achieve other patent protection, the applicant still reserves the claim other features only published in the description and / or drawings. In the references used in the claims, in another embodiment of the object of the main claim characteristics of the corresponding claims, these references do not indicate an abandonment of obtaining an objective protection of the characteristics of the referred claims.

The objects of these claims, however, also form their own inventions which have an independent configuration of the objects of the dependent claims. The invention is also not limited to the embodiments of the description, there are multiple variations and possible modifications within the framework of the invention, especially variants, elements and combinations and / or materials that for example by combination or variation of individual characteristics in combination with the characteristics contained in the general description and in the embodiment as well as in the claims and contained in the drawings, are inventive as well as procedural steps and by combined characteristics lead to a new object or to new procedural steps, insofar as refer to test and work procedures.

Claims (67)

1. NOVELTY OF THE INVENTION Having described the invention as above, the content of the following is claimed as property: CLAIMS 1.- Train or drive rope especially for a motor vehicle that includes a drive unit tai as a combustion machine with a shaft drive as well as at least one electrical machine that is in conjunction of action with the drive shaft, which at least is used as a motor and generator, characterized in that the union of action between the electric machine and the drive shaft presents at least two stages automatically adjusts the operating mode of the separate electrical machine in the start-up and operation phases.
2. 2. Drive train according to claim 1, characterized in that the electric machine in the action joint is disposed between the drive shaft of the drive unit and an input shaft of a power take-off unit such as a mechanism where the power take-off unit, if provided by means of at least one force transmitting unit such as friction collection, Fottinger coupling or torque transformer or the like, is uncoupled from the drive unit.
3. 3. Drive train according to claim 1, characterized in that the electric machine is in action connection with the end of the drive shaft of the drive unit opposite the power take-off unit.
4. 4. Driving train according to one of the preceding claims, characterized in that the axis of rotation of the electric machine is arranged approximately parallel to the axis of rotation of the drive shaft.
5. 5. Drive train according to one of the preceding claims characterized in that the action joint consists of at least one pair of transmission discs and a wrapping agent that joins these in a friction closure.
6. 6. Drive train according to one of the preceding claims characterized in that the transmission discs are formed by discs or belt pulleys and the enclosing means is a band.
7. 7. Driving train according to one of the preceding claims characterized in that at least two transmission discs are formed from at least two pairs of cone discs and is inserted between the cone discs of each pair of cone disc a chain as a wrapping medium in a friction closure.
8. 8. Drive train according to one of the preceding claims characterized in that, the pairs of cone discs allow for the ability of continuous axial displacement from the cone discs of each pair of cone discs on the different driving diameter that is adjusted of the chain, a continuous adjustment of the transmission.
9. 9. Drive train according to one of the preceding claims characterized in that the action joint consists of at least one pair of gears.
10. 10. Drive train according to one of the preceding claims characterized in that the electric machine is used as an initiator for the drive unit.
11. 11. Drive train according to one of the preceding claims characterized in that the electric machine is used for the forward movement of the motor vehicle.
12. 12. Drive train according to one of the preceding claims characterized in that, during the initiation phase of the drive unit the number of rotations of the electric machine is greater than that of the drive unit.
13. 13. Drive train according to one of the preceding claims characterized in that the transmission of the electric machine to the driving unit during the start-up phase is in the range 3: 2 and 10: 1.
14. 14. Drive train according to one of the preceding claims, characterized in that the adjustment of the transmission stages is carried out in dependence on the direction of the moment of rotation.
15. 15. Drive train according to one of the preceding claims characterized in that, in a moment of rotation flow of the drive unit in the direction of the drive unit.
16. 16. Drive train according to one of the preceding claims characterized in that the transmission of the electric machine to the driving unit in the operation as generator is in the range between 2: 1 to 1: 2.
17. 17. Drive train according to one of the preceding claims characterized in that, for the formation of at least two stages of transmission of the action joint is arranged at least one mechanism between the electric machine and the driving unit.
18. 18. Drive train according to one of the preceding claims characterized in that, as at least one mechanism, a planetary mechanism with at least one hollow wheel is provided with at least one sun wheel and at least one planetary wheel.
19. 19. Drive train according to one of the preceding claims characterized in that, as at least one mechanism is provided a stationary mechanism with at least two pairs of gears.
20. 20. Drive train according to one of the preceding claims characterized in that the at least one mechanism for controlling the different transmissions contains at least two assemblies.
21. 21. Drive train according to one of the preceding claims characterized in that the at least one mechanism for controlling at least two transmissions contains a combination of at least one free wheel and at least one coupling.
22. 22. Drive train according to one of the preceding claims characterized in that the at least one mechanism for the control of at least two transmissions, contains at least two free wheels.
23. 23. Drive train according to one of the preceding claims characterized in that at least one of the assemblies is a centrifugal force coupling.
24. 24. Drive train according to one of the preceding claims characterized in that at least one of the couplings is an electromagnetic coupling.
25. 25. Drive train according to one of the preceding claims, characterized in that, together with the at least one switchable mechanism, a fixed adjusted transmission has been provided at the junction of the electric machine and the driving unit.
26. 26.- Drive train according to one of the preceding claims characterized in that the fixed adjusted transmission of the driving unit to the electric machine is in the range of 3: 2 to 5: 1.
27. 27. Drive train according to one of the preceding claims characterized in that the fixed adjusted transmission is formed by a transmission with diameters of the different transmission discs.
28. 28. drive train according to one of the preceding claims characterized in that the fixed transmission is formed by a pair of gears.
29. 29. drive train according to one of the preceding claims characterized in that the hollow wheel of the planetary mechanism is fixedly attached to the rotation with a fixed part in the box or housing.
30. 30. Drive train according to one of the preceding claims characterized in that the first transmission stage is carried out by the driving of the sun wheel by the electric machine and the power take-off through a rod that takes at least a planetary wheel where in the force flow of the first transmission stage the moment of rotation is transferred through a first free wheel provided or a first clutch coupling and a second overrunning free wheel provided in the force flow of a second transmission stage or a corresponding second coupling is disengaged.
31. 31. Drive train according to one of the preceding claims characterized in that the second stage of transmission takes place by the drive of the rod that takes at least one planetary wheel by the driving unit and the power take-off through the wheel from sun to electric machinewhere the first freewheel is overturned or given in case the first coupling is disengaged and the second freewheel or if necessary the second coupling transfers the torque that comes from the driving unit.
32. 32.- drive train according to one of the preceding claims characterized in that the first transmission stage is performed by the drive of a first pair of gears by the electric machine, where in the force flow of the first transmission stage , the moment of rotation is transferred by means of a first freewheel or of a first engaged coupling to a first gear of the first pair of gears and a second freewheel provided in the force flow of a second transmission stage is overexposed or given the case is decoupled from a second coupling provided correspondingly.
33. 33.- Drive train according to one of the preceding claims characterized in that the second transmission stage takes place by the drive of the second pair of gears by the drive unit, where the first free wheel is overrun or if necessary disengaged the first coupling, and the second freewheel or if necessary the second assembly transfers the moment of rotation in the force flow of the second transmission stage.
34. 34. Drive train according to one of the preceding claims characterized in that the first freewheel or, where appropriate, the first coupling in the force flow is arranged before or behind the parts that determine the transmission.
35. 35.- Drive train according to one of the preceding claims characterized in that, the second free wheel or given case the second coupling in the flow of force is arranged before or behind the construction parts that determine the transmission.
36. 36.- Drive train according to one of the preceding claims characterized in that the mechanism for the transmission between the driving unit and the electric machine is arranged in the output shaft of the driving unit or in the input shaft of the unit of power intake.
37. 37.- Drive train according to one of the preceding claims characterized in that the mechanism is arranged radially inward of a rotor of the electric machine.
38. 38.- drive train according to one of the preceding claims characterized in that the mechanism is essentially arranged radially inward of the transmission disc of the electric machine.
39. 39.- Drive train according to one of the preceding claims characterized in that the mechanism is essentially arranged radially inward of a transmission disk of the drive unit that forms the transmission to the electric machine.
40. 40.- Drive train according to one of the preceding claims characterized in that the mechanism is a constituent part of the driving unit and / or is placed in its housing.
41. 41. Drive train according to one of the preceding claims characterized in that the drive shaft of the drive unit and the shaft of the electric machine are rotatable with respect to each other against the effect or action of at least one force buffer under the formation of a damping facility.
42. 42.- drive train according to one of the preceding claims characterized in that a limiter is arranged in the flow of force between the driving unit and the electric machine.
43. 43. Drive train according to one of the preceding claims characterized in that the limiter and / or the damping device is or are arranged radially inwardly of a transmission disk and / or the rotor.
44. 44.- drive train according to one of the preceding claims characterized in that the limiter and / or the damping installation is or are arranged in the drive shaft and / or on the shaft of the electric machine.
45. 45.- Drive train according to one of the preceding claims characterized in that the two transmission stages adjusted in dependence of the direction of moment of rotation is performed by means of a planetary mechanism with gear gears inclined consisting of a hollow wheel rotatable and axially displaceable, at least one planetary wheel arranged in a rod joined to the drive shaft and a sun wheel attached to the transmission disk belonging to the electric machine, where by means of the axial displacement capacity of the hollow wheel it has There is a first transmission stage through a fixed connection of the hollow wheel with a fixed part to the rotation and a second transmission stage by means of a connection of the hollow wheel with the rod.
46. 46.- drive train according to one of the preceding claims characterized in that the first transmission stage is stopped with a higher rotation number than necessary for the start-up process.
47. 47.- drive train according to one of the preceding claims characterized in that the first transmission stage is stopped by means of at least one body placed at the external periphery of the rod where this body by means of the effect of the centrifugal force grasps in a corresponding recess in the inner periphery of the hollow wheel.
48. 48.- drive train according to one of the preceding claims characterized in that at least one body has a conical shape.
49. 49.- Drive train according to one of the preceding claims characterized in that the hollow wheel axially displaceable on both sides has front side means for a form closure with a component of the drive train that does not rotate for stopping by part and on the other hand with the rod.
50. 50.- drive train according to one of the preceding claims characterized in that the means are a gripping gear and / or an agent that forms a friction closure such as friction coatings.
51. 51.- drive train according to one of the preceding claims characterized in that the housing or housing of the mechanism is fixedly connected to the housing of the drive unit.
52. 52.- drive train according to one of the preceding claims characterized in that the mechanism housing is mounted rotatably on the drive shaft and rests on a wrapping tenement arranged through a lever arm provided in the case.
53. 53. - Impuleion train according to one of the preceding claims characterized in that the mechanism case is mounted rotatably on the shaft of the electric machine and rests on a wrap agent tensioner disposed through a lever arm provided in box.
54. 54.- Drive train according to one of the preceding claims characterized in thatThe envelope tensioner adjusts to a basic tension of the surrounding agent and the tension of the surrounding agent depends on the moments.
55. 55.- Drive train according to one of the preceding claims characterized in that the bearing for the mechanism box and / or the bearing for the transmission disk for the output of the drive shaft is disposed within the plane of the wrapping agent.
56. 56.- Drive train according to one of the preceding claims characterized in that the bearing for the mechanism box and / or the bearing for the transmission disk provided in the electric machine shaft is disposed within the plane of the wrapping agent .
57. 57.- Drive train according to one of the preceding claims characterized in that the housing of the mechanism eeta mounted freely rotatable on the impeller shaft and an axis of the transmission disk by ei iado of the drive shaft displaced from the shaft and the mechanism it forms a fixed force lock with the gear connected to the shaft of the transmission disk and the transmission disk on the drive shaft side is connected by means of a wrapping agent to the transmission disk of the electric machine.
58. 58.- Drive train according to one of the preceding claims characterized in that, the mechanism box is mounted freely rotatable on the shaft of the electric machine and on a transmission disk shaft coordinated to the electric machine and displaced from the shaft, and the mechanism forms with a gear fixedly attached to the axis of the transmission disk a flow of force and the transmission disk coordinated to the electric machine is connected by means of a wrapping agent with the transmission disk of the drive shaft.
59. 59.- Drive train according to one of the preceding claims characterized in that, the mechanism is a planetary mechanism.
60. 60.- drive train according to one of the preceding claims characterized in that the planetary mechanism has gears of inclined gears and an axially displaceable rotating hollow wheel, which by means of axial displacement produces a force closure with the rod or with the mechanism box for adjustment or establishment of two different transmission stages.
61. 61.- Drive train according to one of the preceding claims characterized in that, the mechanism casing formed of two pairs of gears with front gears that is rotatable with two transmission stages is mounted on the drive shaft and on the shaft of the transmission disc on the drive shaft side, two gears corresponding to the mentioned pairs of gears are fixed to the rotation and connected with the transmission discs disposed displaceable on the shaft in the drive shaft by way of the impeller shaft and The other two remaining gears are mounted on the drive shaft through opposite freewheels.
62. 62.- Impuleion train according to one of iae claim previously characterized in that the mechanism casing formed of two pairs of gears with front gears is rotatable with two transmission stages on the shaft of the electric machine and the connected transmission disk In a fixed manner with the shaft is placed movably by the shaft axis of the transmission disk and two gears belonging to the mentioned pair of gears are fixed to the rotation with the transmission disc and the other two remaining discs are mounted on the shaft of the shaft. electric machine through free wheels opposite each other.
63. 63.- Drive train according to one of the preceding claims, characterized in that, the axial displacement d between the axis of the transmission disk and the drive shaft or the axis of the electric machine, in reference to a safety factor has such a magnitude that the axis of the transmission disk in an extension of the enclosing medium runs or rotates around the drive shaft or the axis of the electrical machine.
64. 64.- Drive train according to one of the previous claims, characterized in that, it is valid for the displacement of the axis d the condition 20cm >; d > Icm.
65. 65.- drive train according to one of the preceding claims characterized in that the two transmission stages selected by means of the driving direction are formed by two pairs of transmission discs of different diameter that are equipped with respective enveloping means, where each time a first transmieión disk of both pairs of transmission discs, by means of free wheels or ai that do it against each other in what refers to the direction of over rotate or overlook, is mounted on the drive shaft or shaft of the electric machine, and the second drive die belonging to the corresponding transmission pair is fixedly connected to the shaft of the electric machine or to the drive shaft.
66. 66.- drive train according to one of the preceding claims characterized in that the electric machine coaxially next to the end of the drive shaft placed opposite the mechanism for operating the vehicle is arranged around the drive shaft where an output part of the The switching mechanism is automatically linked to the drive shaft and an input part with the rotor in a force lock.
67. 67.- drive train according to one of the preceding claims characterized in that the rod of a turning mechanism is connected to the drive shaft and its sun wheel with the rotor of the electric machine in a force lock