DE10025853A1 - Drive train for automotive vehicle includes coupling members having their coupling states established independently from coupling state of other coupling members - Google Patents

Abstract

Drive train (1) has drive unit (2), exit unit (7), and mobile mass (5) that is connected to drive unit by separation coupling member (4), and to exit unit by starting coupling member (6). Coupling states of coupling members are established independently from coupling state of other coupling members, and are maneuvered by disengaging assembly (16) with the axially movable disengagement device (15). An Independent claim is also included for the assembly method.

Description

The invention relates to a drive train, in particular for a motor vehicle, at least consisting of a drive unit, a flywheel and a Output unit, the flywheel by means of a clutch with the Drive unit and by means of a starting or clutch with the Output unit can be coupled and a method for operating the same.

Powertrains in which a freely rotatable flywheel by means of two Couplings from the drive unit such as the internal combustion engine and from the Output unit such as gears to isolate the momentum are known. Furthermore, drive trains are known in which the rotor is one Electric machine is firmly connected to the flywheel, respectively this forms, so that hybrid drives are possible by means of these arrangements.

Such drive trains generally have double clutches that are used for Switching of the four possible clutch states (open / open, open / closed, closed / open, closed / closed) with two separate  Release systems are equipped for individual actuation of the clutches, so that extensive use of the electric machine, for example, as Starter unit for the internal combustion engine, power generator, partial drive, full drive and as a unit for converting kinetic energy into electrical energy Deceleration of the vehicle when the internal combustion engine is disconnected (Recuperation) is possible. An example of this is DE-OS 44 34 019, the one has such a double clutch with two separate release systems, called. The disadvantage of these double releasers is their high weight, high weight Costs as well as the requirements for the installation space and its variety of parts. Furthermore, these systems also require adjustments on the part of the transmission, primarily because of the radially nested release systems are an additional hollow shaft or a hollow drilled Transmission input shaft in the area of the release system housing require.

Alternatively, solutions with a disengagement system have been proposed which - like shown on the example of DE-OS 29 31 515 - no way to close the starting clutch with the clutch disconnected. This is particularly so then disadvantageous if a vehicle with economical driving style Recovery of the kinetic energy when the vehicle decelerates should be exploited by the vehicle with the starting clutch closed and because of the efficiency of the recuperation reducing  Drag torques decoupled internal combustion engine by means of a Energy recovery process such as the generation of electrical energy is delayed by the electric machine.

The object of the invention is therefore to provide a drive train and a corresponding one Propose a method for its operation, which is lightweight and simple structure allows the vehicle he drives under Operate energy recovery during the deceleration process. A Another task is an inexpensive manufacture and assembly of a Powertrain with an optimization of the number of parts used.

The task is accomplished by a powertrain, especially for motor vehicles, solved, at least from a drive unit, a flywheel element and an output unit, the flywheel element by means of a first clutch as a separating clutch with the drive unit and by means of a second can be coupled as a starting or clutch with the output unit and the two clutches, each with an open and closed clutch condition by means of a single disengagement device with an axial displacement cash releaser are operated, characterized in that the clutch levels of one clutch regardless of the clutch status of the other clutch are adjustable.  

A vehicle can be operated with the proposed drive train, store the kinetic energy in the flywheel element via the flywheel can. You can do this with the disconnect clutch open and the start clutch closed a purely mechanical recuperation can be beneficial by the momentum mass is accelerated by the deceleration process and then at by Opening the isolated clutch flywheel saved the kinetic energy with which the vehicle is started, continued or the Internal combustion engine can be started by the necessary for the process clutch is closed.

For this purpose, it can be advantageous to use an additional flywheel To couple flywheel element. Advantageous embodiments for Koppe flywheels, automatic clutches such as centrifugal and / or magnetic clutches or, for example, gears and / or free-wheeling fe, which decouple part of the flywheel in the train mode and in the thrust driven can couple part of the flywheel. In particular can Here, embodiments that are dependent on the Torque direction allows coupling of the additional flywheel mass chen. For possible configurations, please refer to the registration with the file Refersed to DE 199 16 936.6, hereby the full content of the present Registration is included, the rotor proposed there an electri machine can be replaced by a flywheel or as a flywheel  can work. The additional flywheel mass that can be connected and disconnected can go further towards the output of the gearbox and the flywheel element at the input the gearbox positioned and an over between the two flywheels can be effective. For example, the coupling the additional flywheel mass on the flywheel mass element in the recuperator onsbetrieb and in the start operation by means of a gear, for example, a Um running gear, in which an engagement of the by means of helical teeth Inertia can take place, be particularly advantageous. The additional centrifugal mass coaxial or axially parallel to the drive shaft of the drives be arranged and the power flow via gears, belts, friction surfaces and / or the like. An opposite direction of rotation of the Both flywheels are an advantage.

Furthermore, the design of the couplings can meet the requirements of the Drivetrain must be adjusted. For example, the couplings themselves be known friction and / or positive clutches. In particular, it can be advantageous to have at least one of the two clutches as a friction clutch one axially by means of the release against an axially effective one, the friction handle defining energy storage relocatable pressure plate, an axially fixed Flywheel mass element with at least one friction engagement surface and one axially between pressure plate and flywheel element by means of friction linings in Rei  which can be brought into engagement and rotatably connected to the drive shaft or output shaft provide connected clutch disc.

The disengaging device for the drive train according to the invention has advantages fortunately a single, axially displaceable releaser, which both clutch lungs actuated, that is, when the couplings are designed in such a way that it is closed by axial force, that is be engaged, the one releaser acts on both clutches by by applying an axial force both clutches sequentially and independently of open and close the clutch condition of the other clutch.

It can be particularly advantageous to use a continuous cycle Provide axial displacement of the release, in which all four clutch states de are driven through, resulting in a homogeneous, quick actuation of the clutch lungs, combined with a rational movement of the release can. For example, from a basic state with both clutches in closed or engaged state of the releasers in one direction be be moved, whereby the first, for example, the starting clutch opened net, then opened a second, for example, the disconnect clutch then the starting clutch is closed again. Can advantageously at this point the direction of the release is reversed and the process reversed, namely for the present example in such a way that the  Starting clutch opened again, the separating clutch closed and locked The starting clutch is closed again. From this you can use An axial stroke of the clutch release closed all four clutch states Open / closed, open / closed, closed / open and open / open and in the countermovement immediately and without additional releasers movements are reversed after the release of the release.

It does not matter in which way - apart from the axial direction the force - the clutches are actuated. For example one or both clutches by changing the force ratios on one axially movable pressure plate with the flywheel forming a pressure plate diaphragm spring tensioning plate spring can be actuated by Belleville spring tongues of the Belleville spring or another component connected to it the force on the pressure plate via a one-armed and / or two-armed lever as a function of their axial displacement by means of the release from a neglected visible voltage on the pressure plate with the clutch open to full Measure the effect of the disc spring when the clutch is engaged, opening the clutch can be opened by pulling or pushing the release.

It can also be advantageous if the disengaging device is arranged around the output shaft, for example, a transmission input shaft of a transmission is arranged and the releaser has an approximately circular design around the axis of rotation  surface for the coupling levers actuating the couplings, for example Disc spring tongues with the axial interposition of one of the different ones Relative movements between articulation levers and releas compensating Aus has repository. In some applications, especially when on the intended location for the release device around the output shaft is not enough enough space is available, it can be advantageous to move the releaser in to provide a hollow bore of the output shaft as a push rod and the off rear device axially, for example to the other end of the output shaft relocate.

The disengaging device can be hydraulically known by means of a Master / slave cylinder device, pneumatically or directly electrically operated are given by an electric motor and / or solenoids to the releaser if directly with the participation of a corresponding jerk damping device Shift the release axially. Hydraulic / electrical can be particularly advantageous be combined disengagement devices, the releaser advantageously axially displaced by means of a slave cylinder, the master cylinder being electrical, actuated for example by means of an electromagnet or an electric motor and the control signal for its actuation by a control unit, which to trigger the control signal at least one parameter such as the speed of the Input or output shaft, wheel speed, throttle position of the driver Material supply device of the drive unit, state of charge of the electrical  Energy storage when using an electrical machine around that Flywheel mass element, speed of the rotor of the electrical machine, loading acceleration of the vehicle in the longitudinal and / or transverse direction or the like evaluates, or from a switching signal of the driver, for example from a Shift intention sensor when operating the shift lever in an automatic Coupling can be generated.

It can be particularly advantageous for a drive train of the type described be when a rotor of an elec Tromaschine with the formation of an additional or alternative flywheel is rotationally attached. Such electromas known as starter generators Machines are multifunctional, their range of application through the proposed drive train is additionally expanded. Through the possibility of indenting The clutch and disengaged clutch can, as in the case of the mechani recuperation, the flywheel element with the rotation around it arranged rotor are accelerated when the vehicle decelerates and generates electrical energy by means of the electrical machine in generator operation become. In other exemplary embodiments, a combination of mechanical and / or electrical recuperation are provided, wherein in certain cases only the flywheel element with the rotor and a if necessary, additional flywheel mass is accelerated, for example at low energy consumption and / or full energy storage, or only the rotor  of the electrical machine without a generator as a flywheel can be inclined. For example, there may be severe delays be a part, a possibly existing additional flywheel and the Accelerate electric machine in generator mode. For example at slight gradients or comparable driving situations, it may be appropriate electrical machine not in generator mode or even with low drive to operate and copy any flywheel that may be present peln, or if it has a kinetic energy reserve, to couple, around the vehicle when disconnected and thus the efficiency because of it For example, the drive unit does not affect drag torques moderate speed (sailing).

The operating states of a drive train according to the invention with one around Flywheel arranged electric machine or with one of the drive unit and the output unit such as a transmission by means of the two couplers rotor that can be uncoupled are therefore at least the start function with direct and / or pulse start, the generator operation with drive of the electric machine the drive unit or recuperation and / or the drive function, the Electric machine support the drive unit or the vehicle alone can operate.  

An embodiment of a drive train according to the invention provides one Actuation of the at least two clutches before, in which the or the axially effective men energy storage of the first clutch from the clutch directly and the or Energy storage of the second clutch by means of an axially displaceable, the Pressure plate of the first clutch radially encompassing lever, also known as a clutch can be seen, disengaged. It can be done from before be part if the axially aligned lever parts directly in the area of the outside circumferentially of the pressure plate and are therefore smaller than the radial outer circumference of the rotor or the flywheel the flange part, so that the axially aligned lever parts through in the flange part can reach through provided openings. It can also be beneficial be, not the axially acting energy store for bracing the pressure plate and pressure plate of a clutch but the pressure plate to shift axially even against the effect of the energy store, since in Ab dependence on the design of the coupling of the energy storage axially the opposite side of the pressure plate on the flywheel element or support a component connected to it, for example the rotor can. The two contact surfaces for the friction linings of the clutch discs, from one with the drive shaft and the other with the drive shaft the output shaft can be connected to the isolating from the couplings ble flywheel element provided, which is a flange that rotates can be mounted on the drive shaft or the output shaft, and one  radially outer flywheel, which is also a rotor of an electri machine, can have.

Advantageously, the energy storage devices for axially bracing the Pressure plates and the pressure plates with axially arranged Reibbe were the clutch discs formed from disc springs, which are between one axially non-displaceable component, such as the flywheel mass ment or the rotor and the pressure plate against their spring constant zen and thus the pressure plate, which is axially displaceable, but rotationally flat if connected to the flywheel element, apply it axially. A For this purpose, the diaphragm spring acted upon by the clutch can use diaphragm spring tongues have which are guided radially inwards and on the release bearing of the off can concern. The plate spring can adhere to the flywheel Support senelement to form a one- or two-armed lever, so that with an axial displacement of the clutch, the clutch by Zie hen or press can open.

Correspondingly, for the second, by means of the axially displaceable coupling dec kels operable clutch, which advantageously the separating clutch between Drive unit and flywheel element is a disc spring used the. The clutch cover can be axially on the working area of the Have disengaged coordinated radial area that is radial to the height of the  Ausrückers expanded and in the disk spring tongues distributed over the circumference Similar booms can be structured, which is also applied by the releaser become. Depending on the desired sequence of clutch states the plate spring tongues can be axially spaced. So it turned out to be beneficial proven, the disconnect clutch near the drive unit and the starting clutch to accommodate away from the drive unit. In this arrangement you can the diaphragm spring tongues of the starting clutch axially through the spaces between Boom of the clutch cover to be guided so that this for actuating the Starting clutch before the separating clutch is first acted on by the releaser the. If the starting clutch is disengaged, the separating clutch can be switched off Rückers and the radial boom, which stop at their inner circumference ring can be connected, the clutch cover are disengaged, the Disc spring tongues of the clutch axially between the releaser and the Booms of the clutch cover can be fixed axially. It can be in one another embodiment may also be advantageous, both clutches as drawn To design ne couplings so that the axial entanglement is avoided can.

According to the inventive idea, the clutches are actuated sequentially, preferably starting from a basic state in which both couplers lungs are closed during a successive axial displacement of the end In one direction, first the clutch and then the clutch  can be opened. With a further axial displacement of the release in the starting clutch can be closed again in the same direction by the pressure fixed axially on the clutch cover by means of the plate spring tongues plate is driven against the pressure plate, the friction pads against Effect of the two disc springs of the couplings between the pressure plate and the pressure plate are clamped. This bracing is for transmitting the from the vehicle wheels via the output unit to the starting clutch and from there on the pressure plate of the flywheel element with the flywheel and / or the rotor for recuperation sufficient, a typical performance the electric machine of 5-40 kW, preferably 5-20 kW, in particular 5-10 kW can be advantageous. The energy storage constants of such a coupling arrangement are advantageously designed so that the effective energy Giespeicher constant like that in the previously described embodiment the diaphragm spring constant of the separating clutch taking into account the lever ver Ratios larger than that of the energy storage device, such as the diaphragm spring constant of the An drive clutch is open.

The coupling arrangement is advantageously designed such that the pressure plates for the transmission of a high torque if possible large circumference, that is, immediately radially within the rotor or one Earth rings of the flywheel element are arranged. You can both printing plates have approximately the same circumference. The driving force  axially closer pressure plate can by means of distributed over the circumference Stud bolts, which are distributed over the circumference through corresponding recesses in the Engage the flywheel part and the radially aligned part of the dome can be connected in the same way, connected, at for example screwed, riveted or caulked.

It can be used for the arrangement of the clutches and their transmissible moment be further advantageous if at least one coupling is conically arranged Has friction surfaces with friction linings, the smaller radius of the cone can face in the direction of the drive unit.

Another embodiment according to the inventive concept sees one Drivetrain in front, on the isolatable flywheel element, the radial can carry a rotor outside to form at least one clutch radially inwardly expanded flange part is provided, which is an axially fixed to press plate forms, the pressure plate by means of an axially effective energy memory, which is formed on an at least one contact surface component of the Flywheel element supports, between the flywheel part and the Pressure plate is clamped axially and axially between the pressure plate and the An press plate the friction linings of the clutch disc are arranged at a Friction the torque entered in the flywheel element to the  Drive or output unit or if two clutches are arranged in this Transferred way to both.

An embodiment further developed according to this inventive idea game has a radially inwardly expanded and with the flywheel element connected flange part, one for both energy storage devices like disc springs Forms contact surface to support them, each with an energy store axially supported on one side.

To form an arrangement in which all four clutch states with one Axial movement of the release can be switched, the energy memory for axially bracing the couplings advantageously by means of a Lever mechanism operated, the at least one energy storage device of a clutch lung - preferably the starting or shift clutch - in pull and push direction tion applied. This energy storage device can be advantageous in this Embodiment advantageously a plate spring, depending on the direction of movement of the releaser using one arm and two arm arm to act so that the clutch in a direction of movement release of the release with increasing axial displacement and then in same direction of movement of the release can be closed again. It is understood that with a reverse pressure applied in this way plate the same effect is achieved, in both cases the plate spring in  one step using a one-armed lever and the other step using a two-armed lever is applied.

An exemplary embodiment of a lever arrangement for loading this arrangement can be done in that a contact surface on the pressure plate surface for the disc spring with a medium circumference and on the axially fixed component on the flywheel element radially outside and radially inside this order beginning contact surfaces for the plate spring can be provided, with increasing displacement of the disengagement first the plate spring on the support one and then on the other flywheel-side contact surface can and therefore one arm and one time a two arm Lever to act upon the pressure plate and thereby the clutch first by means of the two-armed lever when the disc spring rests on the radially inner one Pressed contact surface of the axially fixed component and then by means of the einarmi towards the lever when the disc spring rests on the radially outer contact surface is pulled. Accordingly, the clutch is in another embodiment play with the one arm with reverse axial displacement of the release Lever closed and then closed again with the two-armed lever presses.

The second clutch - preferably the disconnect clutch - can during the Axial displacement of the releaser advantageously via one with the Hebelme  Mechanism of the first clutch - preferably the starting clutch - connected NEN lever mechanism can be operated, the clutch depending on the off the guide can be pulled or pressed. The actuation of the separator Coupling takes place according to the inventive idea during the axialver storage of the release in one direction between opening and before renewed closing of the starting clutch, so that in one embodiment in Course of an axial displacement of the release from the clutches with the clutches in the closed state first the pressed starting clutch open by releasing the plate spring, then open the disconnect clutch is pulled and the starting clutch is neither pulled. In the other equipment The closed clutch is reduced by releasing the disk spring opened, the separating clutch by releasing the associated plate spring closed and the starting clutch pressed against the disc spring force. It is understood that according to the inventive idea, a coupling with a one or two-armed actuating lever with a second clutch with a to combine one and two-armed lever, a variety of advantageous An order variants results, all of which are included in the registration.

An exemplary lever mechanism for both clutches can be designed in this way be that a lever device in two parts from a lever system for a clutch tion, for example for the disconnect clutch and a switching state of the other  Coupling like the starting clutch, the two closed switching states points is provided.

The two lever systems are advantageously mounted on one another and axially displaceable against each other, so that when the first Switching state only the corresponding lever system is shifted axially and to Disengaging the separating clutch and engaging the second closed state second lever system can be acted upon by the releaser after one axial distance from the first lever system was overcome and at for example, a stop on the first lever system in the second lever system Coupling process engages.

It can also be advantageous to disengage a lever move an energy storage device, preferably the energy storage device of the separator clutch to ver on the lever system, for example by means of a linkage lengthen to the disengagement of the two clutches to the commute of the Adjusters to adjust. For this purpose said linkage can be from the inner circumference of the Energy storage are extended radially inwards, with one axially clamped axially between the energy store and the linkage me spring the linkage and thus the lever system with the lever system for the second clutch or for the second closed clutch ment state of the second clutch, which in this embodiment directly with  the releaser is coupled to brace axially. For example, at In NEN circumference of the energy storage means of the spring axially from a flange part The releaser must be clamped away in the radial direction in the area of the rotary axis se the drive shaft a second flange part against the direction of force of the spring receives non-positively, the second flange in ver over the circumference shared axial stops of the lever system for the other clutch is attached.

Another embodiment can provide that one of the two couplings gene, preferably the clutch, a functional unit from a friction forms a clutch and a positive clutch, the friction clutch is bridged by means of the positive coupling, so that the friction clutch for smaller torques than the maximum torque of the drive unit and whose torque peaks and / or preferably for the transmission of smaller ones Torques of the electric machine on the drive unit, for example when their start can be interpreted. The positive coupling can be done by means of a similar lever system are disengaged as in one embodiment the drive train with only two friction clutches with the difference that time between the disengagement of the starting clutch and the Rei The clutch is disengaged and after engagement ken of the friction clutch, the positive clutch can be engaged can. It may also be advantageous to transfer only the friction clutch against the torque from the electric machine to the drive unit  ten and the positive coupling only for the transmission of the entire torque to conclude on the output unit.

An embodiment of an arrangement with a positive coupling can vorse hen that over a provided in the lever device pulling wedge arrangement disengageable form fit, for example by means of a toothing between a flange part of the flywheel element and the drive shaft becomes. The axially displaceable pull wedge can be located between the lever system and the pull wedge supporting axially active energy storage axially be acted upon and in the case of axial displacement a radially displaceable profile, such as Radially displaceable pawls of the flange part distributed over the circumference latch the corresponding profile of the drive shaft, preferably without play, whereby the energy storage device tensions the drawing wedge in the direction of positive locking and the pull wedge - against the effect of the energy storage moved - the notching of the profile can cause.

According to another inventive idea, the flywheel can ment, which may include a rotor of an electric machine and or as a pressure plate have friction engagement surfaces for at least one clutch can be rotated, for example by means of a roller bearing, on a housing Most component of the drive unit, for example on one on the housing wall fixed bearing flange to be attached, which in particular for cost reasons  small diameter can be mounted closely radially outside the drive shaft can. The bearing of the flywheel mass element can also be particularly advantageous be fixed to a rotor when the stator of the electric machine is also on the same or a nearby bearing element as the bearing flange is taken, for example, between the rotor and the stator To be able to better define the gap.

Furthermore, the flywheel element can also advantageously on the Input or output shaft can be rotated. Here again the flywheel element carry a rotor of an electric machine, the front may be arranged on the outer circumference of the flywheel element can and the actual flywheel can form while a flange part with connected to the input or output shaft and the rotor radially on the outside is taken, the flange part or separately formed flange parts with a rotor receptacle can be connected, the friction engagement surfaces for at form at least one of the two clutches. A rotatable bearing of the Inertia mass element can be on the drive shaft radially outside the ver screwing with the drive unit, in some cases it can be advantageous, the flange for the rotor or the flywheel element radially inside the drive shaft, preferably by means of a roller bearing Men, radial space gained and lower costs for a small warehouse diameter.  

Since both the output shaft and the drive shaft with the flywheel Senelement are connectable by means of a coupling, is an advantageous Execution given that the clutch discs each turn sig are connected to the input or output shaft. To the end equal to the friction lining wear, both clutch disks can axially leave be stored on the shafts, but it may be advantageous to use only one Clutch disc - preferably the one arranged on the output shaft - axially designed to be relocatable, as via the common release device Wear also an axial compensation on the axially fixed coupling disc can take place. It can be used when using a clutch conical friction linings and correspondingly shaped pressure and pressure plate The friction is particularly advantageous for avoiding double centering Linings on the clutch disc axially elastic, for example by means of Circumferentially extending, axially elastic leaf springs that over the order start with the clutch disc on one end and the on the other Friction lining carriers are firmly connected.

According to the inventive idea, it can still be advantageous in the An drive train at least one device for damping vibrations of the Provide drive unit. The at least one axial and / or wobble movements of the drive shaft, for example to swing  Isolation of axial and / or wobble vibrations of the drive shaft in Attenuate the range below 400 Hz, preferably below 250 Hz and additionally or alternatively, a torsional vibration damper can be provided. In particular emp it is appropriate for an advantageous embodiment example with a fixed with the Drive shaft connected clutch disc and axially elastically connected Friction linings vibration isolation through appropriate design to bring about this elastic connection. Other axial and / or measures to dampen wobble, in particular in loading range of the clutch disc and / or in the area between the clutch disc and the drive shaft, for example in the form of radially extending, axially flexible flange parts, for example radially outside on the output side and radially are connected to the inside of the drive shaft. It can be advantageous be the elastic damping elements friction elements parallel and / or serial assign.

The damping of torsional vibrations can in the drive according to the invention strand in particular between the drive shaft and the clutch and / or between the starting clutch and the output shaft. It can at Arrangement of a torsional vibration damper between the starting clutch and the output shaft may be advantageous in the conventional manner in the Integrate clutch disc, an advantageous embodiment  Main damper and a pre-damper, each with corresponding friction devices gene can have.

With an arrangement of the torsional vibration damper between the drive shaft and the separating clutch, it can be advantageous to use this as a split Flywheel with at least two flywheels distributed over the circumference provide, the two flywheels against the action of in Effective energy storage devices can be rotated relative to one another in the circumferential direction are. Friction devices can be connected in series and / or parallel to these energy stores gene and / or slip clutches.

An embodiment of the invention with a split flywheel can two - namely, for example, a drive-side primary and one from secondary drive flywheel masses with intermediate, in Contain circumferential effective energy storage, the disconnect development in the power flow can be arranged after the divided flywheel, so that the isolatable flywheel element, optionally with the rotor Electric machine another secondary side, of the first secondary side Inertia part that can be uncoupled by means of the separating clutch can form. Both secondary flywheel parts can be se overall flywheel mass can be matched, it being advantageous can, the secondary flywheel in the power flow between the drive unit  and to make the separating clutch minimal or to omit it entirely. Out of this Arrangements in which the split flywheel is a can be advantageous primary flywheel part and the flywheel element and / or the rotor of an electric machine was the secondary flywheel part. The clutch disc with the friction linings of the clutch can be used the primary-side flywheel part, if the flywheel element forms the secondary flywheel. The effective in the circumferential direction Seed energy storage can in the force path between the clutch plate be and the drive unit or in the force path between the clutch disc and the flywheel element. It can also be advantageous to use such Provide energy storage at both locations. For example, such Energy storage in the clutch disc and / or in the pressure plate of the separator clutch can be arranged, each by an output and an on gear part and the output compared to the input part is relatively rotatable.

In the case of a split flywheel design with one in the power flow downstream clutch can connect the clutch disc of the clutch a disc part of the secondary flywheel is firmly attached, For example, on a permanently connected to this, axially to the actual Flywheel adjacent flange.  

The flywheels are preferably superimposed on one another, for example way, a bearing flange can be provided on the drive shaft, which centers is recorded on the primary flywheel and on which at least that isolable flywheel element and possibly the secondary Flywheel in the power flow between the drive unit and the disconnect clutch can be rotatably added.

Another advantageous embodiment provides an isolatable swing mass element with a rotor of an electric machine, in which the energy store the divided flywheel in the area of its outer circumference are not. It can be particularly advantageous if the outer circumference of the Rotors to approximately the same radius as the circumference in the circumferential direction effective energy storage between the two flywheel elements divided flywheel is arranged.

Another exemplary embodiment according to the invention can be used for wear pensation of the friction linings of the clutch discs corresponding devices exhibit. In contrast to two, preference is given to the respective coupling attached wear compensation devices one for both Clutch disks suggested. The device can in particular the starting clutch between the plate spring acting on the clutch and be arranged the clutch cover and a friction lining wear  arranged around the circumference, even depending on wear Adjust lender ramps, the wear by means of a force and / or Travel sensor can be detected. The adjustment to compensate for the Wear of the friction linings of the starting clutch can directly affect that of the friction linings of the disconnect clutch via the compensation of an enlarged clutch path of the starting clutch due to wear on the friction linings the clutch cover shifting the separating clutch. It is understood that in some applications a wear compensation device on the Separating clutch taking into account the changed adjustment conditions can be partaking.

The object of the invention is further achieved by a method for actuating a drive train which consists of at least two units which can be connected to a shaft by means of at least two clutches, with a disengaging device, clutch states of a first and a second clutch being disengaged with an axially disengaging device releasable releasers are operated and the clutch states with the release device

• a) first clutch closed, second clutch closed,
• b) first clutch closed, second clutch opened,
• c) first clutch opened, second clutch opened,
• d) first clutch open, second clutch closed

are switchable.  

It can also be of advantage in this process that the points a) to d) described clutch states a-d sequentially in the order a, b, c, d to switch, the clutch states preferably by means of a axial direction in a continuous forward and backward movement of the release can be switched. It can be particularly advantageous be to design the method so that the coupling states a-d in one Stroke a forward and backward movement of the release can be switched nen. The reverse of the actuation with the sequential clutch states d, c, b, a can occur in the backward movement, causing the off continuous forward and backward in the course of the actuation of the clutch states Describes backward cycles.

Furthermore, a method can be advantageous in which the first clutch is a Separating clutch is, which couples the two units with each other in a force-locking manner and the second clutch is a starting clutch that depends on the aggregates coupling of the disconnect clutch with an output shaft and / or the two units an internal combustion engine and an electric machine ne are. It can also be advantageous to use just one instead of the electric machine To provide flywheel element by storing kinetic Energy, for example, both the torque on the internal combustion engine their start, as well as on the output unit, such as a transmission  with drive wheels following in the power flow, for example for driving them can transmit.

For example, a method can be carried out such that starting from a starting point at which both clutches are closed, the actuators at least one direction of the couplings against the axial action of an energy store, the at least one energy store being axial can be effectively provided for bracing a clutch and vorzugwei se at least two axially effective energy stores such as disc springs are provided can be one of which is an axially displaceable pressure plate Clutch applied and thus a frictional engagement between friction linings to be coupled shaft or unit on the one hand and the pressure and pressure plate a shaft or an aggregate. The actuation of the clutches via the deflection of the axially active energy store can be according to the method by means of a lever by pulling and / or pressing this by means of the release gene.

The invention is explained in more detail with reference to FIGS. 1 to 8. Show

Fig. 1 shows a schematic arrangement of a drive train of the invention,

Fig. 2 shows a partial section of an exemplary embodiment of a powertrain

Fig. 3 is a partial section of an exemplary embodiment of a powertrain

Fig. 4 is a partial section of another embodiment,

FIG. 5a-d are partial sections of the embodiment shown in Fig. 2 with the adjustable coupling states,

FIGS. 6a-d are partial sections of the embodiment shown in Fig. 4 with the adjustable coupling states,

Fig. 7a-b a double controllable clutch in two embodiments in partial section and

Fig. 8a-b details of an actuator of a positive coupling.

Fig. 1 shows a schematically illustrated embodiment of a drive train 1 according to the invention with a drive unit 2 , which can be an internal combustion engine and by means of a drive shaft 3 outputs torque to a first clutch 4 , which makes the drive unit 2 couplable with a flywheel element 5 as a separating clutch. The flywheel element 5 can be connected by means of a second clutch 6 , which can have the function of a starting clutch, to the output unit 7 , which can be a speed change transmission, such as an automatically or manually operated manual transmission, an automatic step transmission, a belt transmission (CVT) or the like, in the case of a manual transmission, the clutch can also be used as a clutch when changing gear.

The output shaft 8 or transmission input shaft, which is connected in a rotationally fixed manner to the clutch 6, feeds the torque introduced by the drive unit 2 into the output unit 7 , from where it becomes dependent on the gear ratio in the output unit 7 via the transmission output shaft 9 and the differential 10 the drive wheels 11 are diverted, the drive shown also being a four-wheel drive in a manner known per se.

By means of the two couplings 4, 6, the flywheel mass element 5 consisting of a connecting member such as flange portion 5a and a preferably radially outwardly provided flywheel 5 b of the drive unit 2 and the output unit 7 are isolated and free to rotate, whereby during acceleration of the flywheel mass element 5 stored by the drive unit 2 with at least the disconnect clutch 4 or by the output unit 7 , for example when the vehicle decelerates and the start clutch is closed by transmitting kinetic energy, rotational energy, and then again to the drive unit 2 , for example to start it and / or to the output unit 7 can be given as a drive aid.

It will be appreciated that it may be of great advantage to the flywheel 5 b of the flywheel mass element 5 by a rotor 12 of an electric machine to replace 13, whereby the Schwungnutzeffekt can be achieved by further advantageous embodiments, the rotor 12 radially inwardly of the housing firmly to the Drive unit 2 and / or stator 14 attached to the output unit 7 is arranged. In some embodiments, the stator 14 can be arranged radially inside the rotor 12 , in which case the rotor 12 encompasses the stator 14 radially inward via corresponding connecting means.

Exemplary embodiments with an electric machine 13 can, for example, additionally generate electrical energy from the kinetic energy of the vehicle by operating the electric machine 13 as a generator when the starting clutch 6 is closed, as a result of which it is possible to choose between utilization of the recuperation energy in an electrical and / or mechanical manner. It is understood that in this case it can also be advantageous to decouple the drive unit 2 with its drag torque in order to increase the efficiency of the energy conversion, it also being possible to disconnect the clutch before or simultaneously with the use of the vehicle brakes for faster deceleration 4 close and use the drag torque to decelerate the vehicle. Furthermore, by means of the electric machine 13, a direct or pulse start of the drive unit 2 and an operation of the vehicle that supports the drive unit 2 or is possible alone.

Furthermore, when the starting clutch 6 is preferably open, the drive unit 2 can be started in motor mode independently of the rotational energy stored in the flywheel element 5 by means of the electric machine 13 , optionally and, for example, as a function of the outside temperature and / or the temperature of the drive unit 2 by means of a direct start when the clutch 4 is closed , an impulse start when the clutch 4 is initially open to accelerate the flywheel element and then close the clutch 4 , the electric machine 13 being switched off after the clutch 4 is closed , or may continue to have a driving effect when the clutch 4 is closed when the starting behavior is difficult.

For this purpose, the clutches 4 , 6 are actuated accordingly by the axially displaceable releaser 15 as part of the disengaging device 16 . The disengaging device 16 can be provided directly axially between the drive unit 2 and the driven unit 7 , preferably axially between the clutch 6 and the driven unit 7 and / or coaxially around the driven shaft 8 , the releaser 15 advantageously directly on the clutch 6 can act, or at another point, for example at the end of the output shaft 8 facing away from the clutch 6 , the disengagement movement of the disengagement 15 being transmitted to the clutches 4 , 6 by appropriate means, for example a push or pull rod guided in the hollow drive shaft 8 for this purpose becomes.

The release system is controlled and supplied by a supply device 17 . In the simplest case, the supply device 17 can be a pressure supply device, Bowden cable or the like, which, upon receipt of a request signal for actuating one or both clutches 4 , 6, actuates the disengaging device 16 and shifts the releaser 15 accordingly. It goes without saying that the supply unit 17 and the disengaging device 15 can be standardized into one component and this unit can be accommodated elsewhere in the vehicle, so that only the releaser 15 , for example as a slave cylinder unit of a hydraulic disengaging device 16 , for example operated by an electric motor, in the area the couplings 4 , 6 is housed.

To actuate the two clutches 4 , 6 by the release device 15 , lever devices 19 , 20 are provided, which are actuated by the release device 15 in such a way that the clutches 4 , 6 are preferably disengaged sequentially. Both clutches 4 , 6 can be disengaged during the course of an axial release stroke, and clutch 4 can be engaged again when clutch 6 is open. In this way, all clutch states of the two clutches 4 , 6 can be switched by means of a release stroke.

The clutch states are preferably switched according to the sequence a, b, c, d, the following applies to the individual clutch states:

• a) separating clutch 4 closed, starting clutch 6 closed,
• b) separating clutch 4 closed, starting clutch 6 open,
• c) separating clutch 4 opened, starting clutch 6 opened,
• d) Separating clutch 4 open, starting clutch 6 closed.

The individual clutch states are used, for example, in the following operating states of the vehicle:
Clutch condition a while driving;
Coupling state b when the drive unit 2 starts, for charging the electrical energy store (not shown) by the drive unit 2 and / or during the gear change in a manual transmission 7 ;
Coupling state c during a stop of the vehicle, flywheel operation of the flywheel mass element 5 , acceleration of the flywheel mass element 5 or of the rotor 12 by the electric machine 13 ;
Coupling state d for recuperation when the drive unit 2 is preferably switched off.

A possible driving cycle of a vehicle with an exemplary drive train 1 according to the invention with a rotor 12 as a flywheel element 5 and a manual transmission 7 is designed as follows, for example, with clutch states in parentheses:
Vehicle is stationary (c), drive unit 2 is started (b), vehicle is driving (a), shifting (b), vehicle is driving (a), recuperation (d), vehicle is driving (a), recuperation (d), vehicle is holding ( c).

FIG. 2 shows an embodiment 101 of the drive train 1 of FIG. 1, in which only the arrangement of the area axially between the drive and driven unit is shown. This region is formed by the flywheel mass element 105, which can be isolated from the output unit and the drive unit, with a rotor 112 of an electric machine, the stator of which is not shown in more detail, and the two clutches 104 , 106 .

The flywheel element 105 has a radially extending disk part 155 which is rotatably supported by a roller bearing 150 and axially fixed on an axially formed shoulder 153 of a flange part 132 which is connected to the drive shaft 103 via the screws 151 , the bearing being immediate takes place radially outside the screws 151 , but can also advantageously take place radially inside the screws 151 . The bearing 151 is axially fixed by means of the retaining tabs 154 riveted to the flange part 132 . May be at the outer periphery of the disc part 155, an axially extending tubular flange 156 is provided for receiving the rotor 112 integrally formed on the disc member 155 or connected as a separate component with this as welded, bolted and / or riveted and for the axial fixing of the rotor 112 has two stops 156 a, 156 b. At the end of the flange 156 facing the drive shaft 103 there is also a radially inwardly widened extension 157 with a circumferential or ring-shaped bead 157 a for the bearing of the energy store 158 acting axially on the pressure plate 130 of the separating clutch 104 , by means of dowel pins 157 b, rivets, screws, Bolts or the like attached.

In the flange part 155 are provided for each clutch 104 , 106 to form the frictional engagement of the two clutches 104 , 106 with the friction linings 137 and 138, respectively, friction surfaces 134 , 135 and complementary friction surfaces 130 a, 131 a in the pressure plates 130 , 131 . The pressure plate 131 of the starting clutch 106 is opposed to the axial effect of an axially effective energy store such as the plate spring 159 on an annular bead provided for this purpose or annular bead segments 131 distributed over the circumference when the clutch 106 is engaged with the flange part 155 with the friction linings 138 axially interposed to form the frictional engagement tense. The plate spring 159 is axially supported on an axially effective energy store such as sensor spring 160 , which in turn is supported by means of an outer profile 160 a on corresponding recesses 161 a in the inner peripheral region of the clutch cover 161 formed axially in the direction of the drive shaft 103 against the action of the plate spring 159 . The radially inwardly extended plate spring tongues 162 of the plate spring 159 are acted upon axially by the release bearing 163 of the release device (not shown in more detail) and form a two-armed lever with the pivot point at the contact 164 with the sensor spring 160 . The pressure plate 131 is axially displaceable and rotationally fixed in the circumferential direction by means of the circumferentially aligned leaf springs 165 on the clutch cover 161 , one end of the leaf springs 165 on the pressure plate 131 by means of the rivets 166 distributed over the circumference and the other end on the clutch cover by means of rivets not shown is attached. It goes without saying that other fastening means such as screws, rivet warts provided at least in the clutch cover 161 , which are compressed after the leaf springs 165 have been inserted, can be advantageous.

The friction linings 138 of the clutch disc 133 are connected to it via the friction lining carrier 140 , for example riveted. The clutch disc 133 is equipped in the exemplary embodiment shown with a two-stage torsional vibration damper 133 a with a main damper stage 133 b and a pre-damper stage 133 c and the associated friction devices. Such torsional vibration dampers are known per se. A torsional vibration damper which essentially corresponds to the present exemplary embodiment is described in more detail in the application DE 198 20 354 and is hereby fully incorporated into the application described here. It goes without saying that clutch discs of a different design, for example without a damper or with only one or more damper stages, can also be advantageous. The hub 133 d of the clutch disc 133 is connected in a rotationally fixed manner to the output shaft, for example to the transmission input shaft 108 of the following transmission (not shown in more detail) in the power flow.

The clutch cover 161 is provided so as to be axially displaceable for actuating the clutch 104 , wherein in the region of its outer circumference by means of fastening means such as screws 167 b, rivets and / or the like, bolts 167 distributed over the circumference and fastened in the axial direction to the pressure plate 130 are fastened by grasp corresponding openings 168 in the flange part 155 and are connected to the pressure plate 130 in a rotationally fixed and axially fixed manner, for example with an external thread 167 a provided on the bolts 167 .

By axially acting on the plate spring tongues 162 through the release bearing 163 , the clutch 106 is disengaged, the plate spring 159 being clamped axially against the clutch cover 161 , which is supported on the flange part 155 via the pressure plate 130 and the friction linings 137 .

The clutch 104 is disengaged if, after the axial release of the release bearing 163, the plate spring tongues 162 are pressed axially against a collar 169 provided on the inner circumference of the clutch cover 161 when the clutch 106 is disengaged and the release bearing 163 is further axially displaced in the same direction. With the necessary disengagement force, the clutch cover 161 is then axially displaced, taking the pressure plate 131 of the clutch 106 with it, against the spring constant of the plate spring 158 , as a result of which the bracing and thus the frictional engagement between the pressure plate 130 and the flange part 155 and the axially intermediate friction linings 137 will be annulled. This results in a state in which both clutches 104 , 106 are open. In this state, no torque is transmitted from the drive unit to the flange part 155 and vice versa by the friction linings 137 via the friction lining carriers 139 , which are connected in a rotationally fixed and axially displaceable manner to the flange part 132 of the drive shaft 103 via leaf springs 170 which are similar in terms of their arrangement to the leaf springs 165 .

If the release bearing is moved axially further, the distance between the axially fixed flange part 155 and the pressure plate 131 decreases again and the frictional engagement of the clutch 106 is formed again while the clutch 104 remains open. The frictional engagement is determined by the two spring constants of the two plate springs 158 , 159 and can be designed so that it the maximum torque of the electric machine with its rotor 112 on the output shaft 108 or a corresponding torque from the drive shaft 108 in the case of recuperation via the Friction linings 138 can be transferred to the rotor 112 .

The clutch 104 is provided in this embodiment for optimizing the transmitted torque which includes the torque peaks of the drive unit as a result of torsional vibrations as a cone clutch 104th The friction surfaces 130a, 134 are thus inclined from the direction of rotation plane and the friction lining 139 are adjusted accordingly and axially displaced axially in order to avoid a double centering of the flange 132 on the drive shaft 103 and the friction pads 137 frictionally engaged on the leaf springs 170th It is understood that the clutch 104 can also be implemented as a conventional clutch or as a multi-disc clutch and / or torsional vibrations can be reduced or eliminated by means of corresponding torsional vibration dampers by means of corresponding power flow between the drive unit and the separating clutch 104 .

The arrangement shown also has a wear adjustment, in particular for the wear of the friction linings 137 , 138 . It is particularly advantageous that only one wear adjustment device 180 acts on the friction linings 137 , 138 of both clutches 104 , 106 . In this exemplary embodiment, the device 180 is effective as a function of a force sensor such as sensor spring 160 . In further exemplary embodiments, a wear adjustment device that is effective as a function of a displacement sensor that detects the wear of the friction linings can also be advantageous. The sensor spring 160 of the example shown migrates when worn by a as a result of b with a more obtuse angle of the cams 131 employed disc spring 159 increased release load to the diaphragm spring fingers 162 axially toward the drive shaft 103, and outputs thus holding down the clutch 106 a, the plate spring 159 axially of Sensor spring 160 opposing at the pivot point 164 supporting ramp ring 181 game, whereupon this compensates for the game by a circumferential rotation by ramps 181 a formed in the axial direction and distributed over the circumference making contact with the plate spring 159 again. The circumferential rotation of the ramp ring 181 is supported by energy stores 182 which act in the circumferential direction and which act on the one hand on radially aligned brackets 181 b of the ramp ring 181 and on the other hand are supported on loading devices 161 b of the clutch cover 161 , the energy stores 182 being in window-shaped openings in the clutch cover 161 can be accommodated and a circumferential boundary of the window-shaped openings forms the loading device 161 b.

Fig. 3 shows a section of an embodiment in which the two clutches 204 , 206 and the flywheel element 205 with the rotor 212 are arranged in principle as shown and described in FIG. 2, whereby to reduce torsional vibrations of the drive unit in the power flow between the drive shaft 203 and the separating clutch 204, a torsional vibration damper 290 is provided. In the shown embodiment in a torsional vibration damper falls into the clutch plate 233 away which thereby becomes simpler and merely of a rotary circuit to the transmission input shaft 208 producing hub 233 c and a with this integral flange portion 233 a with apertures 233 b for the passage of assembly tools for the Screws 251 for mounting the entire assembly 201 on the drive shaft 203 and the radially outer friction lining carriers 240 with the friction linings 238 . It is understood that in special applications a torsional vibration damper can also be provided in the clutch disc 233 .

The torsional vibration damper 290 is received axially between the drive shaft 203 and the rotor 212 and as a split flywheel with a disk part 291 mounted on the drive shaft 203 as the first, mass on the primary side and a second pulley part 292 as the second, mass on the secondary side, the disk parts 291 , 292 on top of each other are stored and a further flywheel 292 a can be connected to this at least in a rotationally locking manner. The two disk parts 291 , 292 are relatively rotatable against the effect of the energy stores 293, which is provided at least in the circumferential direction. It goes without saying that the second flywheel mass can also be formed by the flywheel mass element 205 , so that the disk part 292 and / or the flywheel mass 292 a can be omitted. The flywheel mass element 205 can be coupled to the disk part 292 via the disconnect clutch 204 , the flange part 232 with the friction lining carrier 239 and the friction linings 237 forming a frictional engagement with the flywheel mass element 205 and being rotatable relative to the disk part 291 against the effect of the energy store 293 . The separating clutch 204 can be designed so that it slips when there are strong torque surges and has the function of a slip clutch.

In the exemplary embodiment 201 shown, the disk part 291 is received axially between the latter and a bearing flange 294 by means of the screws 251 on the drive shaft 203 , the disk part 291 having an axially formed shoulder 291 a in the region of its inner circumference for centering the bearing flange 294 . The disk portion 291 is radially outwardly connected by means of another with it, for example welded annular flange 291 c for forming an energy storage 293, the short compression coil springs or a large extent - for example, approximately half of the circumference - extending, advantageously to approximately the insert diameter pre-bent bow springs be and can be nested, receiving annular bead 291 b formed in which by means of the constrictions 291 d, 291 e distributed over the circumference, corresponding to the number of energy storage 293 distributed over the circumference, corresponding chambers 295 , which can be at least partially filled with lubricant and radially outside can have a wear protection shell radially between the chamber wall and the energy stores, are provided for receiving the energy stores 293 , the constrictions 291 d, 291 e also acting as loading devices for one side of the energy store icher 293 serve in the circumferential direction.

The other side of the energy store 293 is acted upon by the secondary-side disk part 292 by means of radial arms 297 which engage radially inside into the chamber 295 which is open here. In the further course radially inward, the disk part 292 has openings 292 b distributed over the circumference and engage in the corresponding axially shaped cams 292 c of the flywheel 292 a, as a result of which a rotational connection is established between the disk part 292 and the flywheel 292 a. Radially within the cams 292 c are in the flywheel 292 a openings 292 d distributed over the circumference, which spatially form openings 292 b ventilation openings for the clutch 204 , it may also be useful, the openings 292 d radially outside, for example approximately to be arranged at the same radial height as the friction linings 237 of the clutch 204 and to subsequently arrange the cams 292 c radially on the inside. Furthermore, differently designed connections between the flywheel 292 a and the disk part 292 with a corresponding design of the openings 292 b, 292 d can be advantageous.

The friction device 298 is provided radially on the inside between the disk part 292 and the bearing flange 294 . For this purpose, the disc part 292 for the rotationally fixed reception of the friction disc 292 f has an internal profile 292 e, such as internal toothing, which axially with the interposition of a spring 298 a and a friction control disc 298 b engaging in the toothing 294 a of the bearing flange 294, preferably with a backlash, between the disc part 291 and is connected to the bearing flange 294 rotatably connected radially outwardly widening annular flange 294 b.

The secondary part, consisting of disc part 292 and flywheel mass 292 a, is supported on the bearing flange 294 by means of a roller bearing 299 , and a sliding bearing can also be provided to accommodate it. Axially offset and the flange portion 255 is mounted of the inertia member 205 by means of the roller bearing 250 on the same bearing flange. The two parts 292 a, 255 are supported at different diameters radially within the receptacle of the bearing flange on the disk part 291 . If the centrifugal mass 292 a is omitted, there is advantageously no need for mounting and the centrifugal mass element 205 , which acts as a secondary part, can be mounted on the bearing flange 294 .

The flange part 232 receiving the friction linings 237 is rotationally fixed and centered on the flywheel 292 a by means of the screws 251 a.

With regard to its material thickness and shape, the disk part 291 can be designed such that it has axial flexibility to reduce or isolate axial vibrations or wobble vibrations of the drive shaft 203 . For example, the openings 291 f provided for ventilation, in particular of the coupling 204 , can be designed such that the required axial flexibility is preferably determined by the remaining webs between the openings 291 f. In order to prevent the vibrations from propagating into the secondary part, for example into the disc part 292 , the two disc parts 291 , 292 have a corresponding axial play, which is ensured by an axially active energy store, for example the diaphragm spring attached to the disc part 291 by means of lugs 296 a distributed over the circumference 296 , which can also be provided for the sealing function for the chamber 295 , is fixed, the energy store 296 being able to form a friction torque, for example in the radial direction, due to its compression, as a result of which a damping device with a friction device against axial and / or wobble vibrations of the drive shaft 203 can be proposed.

FIG. 4 shows a further exemplary embodiment of a clutch unit 301 , which is arranged in clutch bell 307 a of a transmission (not shown in more detail) and consists of separating clutch 304 , starting clutch 306 and flywheel element 305 with rotor 312 of an electric machine (not shown).

The flywheel element 305 can be rotated by means of the flange part 355 on the drive shaft 303 or, as shown here, on a bearing flange 394 fastened to the drive shaft 303 by means of the screws 351 and preferably centered on this by means of a roller bearing 350 , the bearing 350 using a disk 394 a , which is screwed to the bearing flange 394, preferably on the axis of rotation, is axially secured thereon. In the further course towards the radially outward, openings 355 a distributed over the circumference are provided in the flange part 355 for the passage of the assembly tools for the screws 351 . Radially outside of the screws 351 , the flange part 355 engages around them and forms an axially extending section 385 with the form-fitting coupling 386 , which positively and separably connects the bearing flange 394 to the flange part 355 . The function and further details can be seen from FIGS. 8a and 8b.

Fig. 8a shows the form-locking coupling 386 in longitudinal section with the bearing flange 394 , which has an outer profile 394 b, in the axially displaced over the circumference of pulling wedges 386 c formed by a radially displaceable pawls 386 b distributed over the circumference complementary inner profile 386 a by means of e 23793 00070 552 001000280000000200012000285912368200040 0002010025853 00004 23674 by moving along the ramp 386 d formed by both parts 386 c, 386 b radially inward. The pawls engage through corresponding openings provided in the axially formed section 385 of the flange part 355 . The pawls 386 b can be moved back with the pulling wedges 386 c retracted in order to open the form-fitting coupling 386 by means of an energy storage and / or centrifugal force which is provided for this purpose and is not shown in detail.

Fig. 8b shows sections 386 e of the form-locking coupling 386 shown in Fig. 8a in cross section in the engaged state, in which the pull wedge 386 c presses the inner profile 386 a of the pawl 386 b into the outer profile 394 b of the bearing flange 394 , the pawl 386 b is radially displaced radially through an opening in the axially formed section 385 . Such cutouts 386 e can form the form-fit coupling distributed over the circumference, one to twelve, preferably three to eight cutouts 386 e being advantageous.

In the further course of the flange part 355 , as shown in FIG. 4, the axially aligned section 385 is followed by a substantially radially aligned section 387 with an axial projection 388 in the outer peripheral region, on the front side of which a receptacle 389 by means of a radially extending flange part 389 e is attached to the rotor 312 , for example screwed, riveted or the like. The receptacle 389 encloses the rotor 312 radial, forms an axial stop 389 for a rotor 312, and is commonly connected to a pressure plate 390 as an annular flange executed for the coupling 304 to the rotor 312th It may be advantageous to screw the pressure plate 391 for the coupling 306 , which forms the stop 392 for the rotor 312 on the opposite side, to the rotor receptacle 389 and the pressure plate 390 by means of the continuous screws 312 a distributed over the circumference, whereby the latter can have a thread for the screw connection for this purpose and in principle the guidance of the screws 312 from the pressure plate 390 to the pressure plate 391 which is then equipped with a thread can also be expedient.

In the radially inwardly oriented flange part 389 a of the rotor receptacle 389 , on the side facing the clutch 304, an annular bead or annular bead segments 389 b are provided on the radially outer side for engaging the plate spring 358 , which presses the pressure plate 330 by means of the cams which are located radially further inward and distributed over the circumference 330 a under formation of a one-armed lever against the pressure plate 390 with the axially intermediate friction linings 337 braced, so that it is a drawn clutch 304 , which is by means of an axial displacement of the clutch 315 away from the clutch 304 via the lever device 319 , the Disengagement of the clutch 304 and the positive clutch 386 is coordinated so that the clutch 304 initiates a slipping disengagement or engagement process and then closes or opens the positive clutch 386 , so that the clutch 304 does not have to be designed for the maximum torque of the drive unit.

On the side of the flange part 389 e facing the starting clutch 306 , two ring beads, ring bead segments or cams 389 c, 389 d distributed over the circumference are provided with different diameters, the cams 331 a of the pressure plate 331 distributed over the circumference radially between the cams 389 c, 389 d is arranged.

FIGS. 7a, 7b show two possible exemplary embodiments of a clutch 306 actuated in this way, the example shown in FIG. 7a being used in FIG. 4. Between the segments 389 c, 389 d, on the one hand, and the cams 331 a, on the other hand, the plate spring 359 can be clamped as a function of the position of the release mechanism 315 ( FIG. 4), so that the clutch 306 pressed in this case when the plate spring 359 is under Formation of a two-armed lever on the radially inner cams 389 d supports, with a displacement of the release 315 in the direction of clutch 306 and with an axial displacement away from the clutch 306 , if the plate spring 359 on the radially outer cams 389 d to form a single arm Lever supports, is pressed. It goes without saying that the pressure plate 331 , like the pressure plate 330 , is connected axially displaceably and non-rotatably to the pressure plate 391 or 391 by means not shown, such as, for example, the leaf springs connecting the pressure plate 330 or 331 and the pressure plates 390 or 391.

Fig. 7b shows an embodiment of a pressed-coupling 306 ', in which by means of the plate spring 359', the pressure plate 331 'with the pressure plate 391' with the interposition of the friction linings 338 'is tightened, the pressure plate 331' against the action of the plate spring 359 ' to disengage the clutch 306 'by means of an axial displacement of the preferably rigid lever 359 a, which is supported in one direction on the cams 389 c' and in the other direction on the cams 389 d, is axially displaced and the lever advances over the circumference distributed cams 331 a 'in the direction of the pressure plate displacement against the action of the plate spring 359 '.

The torque is transferred to and from the flywheel element 305 between the drive shaft 305 and the latter via the friction lining carrier 339, which receives the friction linings 337 radially on the outside and is connected to the bearing flange 394 in a rotationally fixed manner, for example riveted. An axial adjustment of the friction linings to the pressure plate 390 or pressure plate 330 is possible via the material thickness of the friction lining carrier. Between the flywheel element 305 and the output shaft, a clutch disc 333 is provided, which is only roughly indicated here, and which is accommodated in a rotationally fixed and axially displaceable manner by means of the hub 333 d. The torque transmission when the clutch 306 is effected by means of the radially arranged friction linings 338, which via the friction lining 340 and an adjoining hub flange 333 e initiate the torque d in the hub 333, wherein in the power flow between the friction lining 340 and the hub 333 d, a damping device 333 b with, for example, a main damper and optionally a pre-damper and / or a friction device as known per se. For further possibilities of damper arrangements in this exemplary embodiment, reference is made to FIGS . 2 and 3, wherein the arrangement of a divided flywheel in this exemplary embodiment can take place in that, for example, the area of the pressure plate 390 is provided with loading means for an end of energy stores that are effective over the circumference is, while the other end of a rotatably connected to the drive shaft 303 or a component connected to it, such as the flange 303 a, which in the example shown is a pulse generator for controlling the drive unit, for example an ignition marking ring with radially outer markings is and would have to be adjusted with respect to the material thickness, is applied by means of appropriately designed loading means.

The lever device 361 for actuating the two clutches 304 , 306 is released from the release mechanism 315 with a non-rotating release lever 315 a, which is mounted on a seat 315 c rotating with the output shaft 308 by means of a roller bearing 315 b, the release lever 315 a using a - Not shown - Actuator, for example an electric motor or a hydraulic unit, can be acted upon with force in both directions and can thus be actively displaced axially in both directions.

The disengagement movements are transmitted from the disengagement lever 315 a via the receptacle 315 c to axially aligned circumferentially distributed bolts 367 which are connected axially and in a rotationally fixed manner and engage through openings 333 f which are correspondingly recessed in the hub 333 d. In further exemplary embodiments, it may be advantageous to design the access to an actuating device such as, for example, plate spring tongues of a clutch, for example the couplings 304 , 306 , from the release lever or a release bearing in such a way that a pressure ring provides a contact surface for the release bearing and in the direction of the actuation lever or the disc spring tongues distributed over the circumference, axially aligned pressure pins, which are axially guided radially between the hub 333 d and the output shaft 308 in the toothing. It may be advantageous to incorporate corresponding axial guides for the pressure pins in the output shaft 308 , for example to mill them in and / or to guide the pressure pins in the tooth gaps of the toothing 308 a and accordingly to cut out the teeth of the hub 333 d at this point. The pressure pins can then directly or expediently act axially at their free end via a receptacle which can be rotated by means of a roller bearing on the actuating lever or on the plate spring tongues for actuating the plate spring tensioning the pressure plate of the clutch. It goes without saying that the proposed solution for actuating each double clutch, in which a clutch disc 333 is arranged axially between the releaser 315 and the actuating lever 365 or the plate spring tongues of a plate spring 359 , can be advantageous.

In the exemplary embodiment 301 explained in more detail in FIG. 4, the bolts 367 are firmly connected at their end remote from the release lever 315 a to an annular receptacle 364 on which the actuating lever 365 for the plate spring 359 is axially fixed by means of the roller bearing 364 a and opposite the receptacle 364 is rotatably received. The actuating lever 365 acts axially on the plate spring 359 by means of axially bent tongues 365 a distributed over the circumference when the release mechanism 315 is displaced in the direction of the drive shaft 303 and thereby presses the clutch 306 by the plate spring being supported on the cams 331 as a pivot point and the pressure plate 331 clamped to the cams 389 d with the friction linings 338 and the pressure plate 391 . The release position selected here is the extreme position with regard to the axial displacement of the release 315 in the direction of the drive shaft 303 .

Passing through the operating lever 365 , radially within the cranked tongues 365 a, further axially displaceable bolts 366 distributed over the circumference are provided, each with stops 366 a, 366 b provided at their ends. In the event of an axial displacement of the release mechanism 315 away from the drive shaft 303 , the tensioning of the plate spring 359 is released by the tongues 365 a and the starting clutch 306 is disengaged again and the actuating lever 365 strikes the stop 366 b and takes the bolt 366 b with it, which causes the on the stop 366 a adjoining tongues 368 a of the actuating lever 368 for disengaging the separating clutch 304 and the positive coupling 386 are taken along and an axial displacement of the actuating lever 319 , which is axially fixedly connected to the actuating lever 368 via a stop 319 a, counteracts the axial action of the plate spring 319 b, which is clamped between the clutch actuator spring 358 and the actuating lever 319 , is effected. By this axial displacement of the actuating lever 319 , which acts as a pull wedge 386 d ( Fig. 8a), the positive clutch 386 is disengaged and the actuating lever 319 with the axial interposition of the plate spring 319 b, the clutch actuator spring 358 is lifted from the cams 330 a of the pressure plate 330 and thus the Clutch 304 opened. With further axial displacement of the release mechanism 315 away from the drive shaft 303 , the plate spring 359 of the clutch 306 strikes the stop 366 a and braces the pressure plate 331 with the friction linings 338 by being supported on the cams 389 c to form a one-armed lever and on the Cam 331 acts on the pressure plate 331 and thus engages the clutch 306 .

FIGS. 5a-5c show the adjustable coupling states a, b, c, d of the coupling assembly 101 to the description of the method according to the invention. The four coupling states a, b, c, d are connected by means of the releaser 115 in a stroke in the direction of the drive shaft 103 switchably and directly reversible by a rearward displacement of the releaser 115, that is, a cycle of a continuous advantages and Rückwärstbewegung the releaser 115, the order of clutch states a, b, c, d, c, b, a switch.

In clutch state a of FIG. 5a, both clutches 104 , 106 are closed and the clutch release 115 is in its most distant position relative to the drive shaft 103 . In this state a, the vehicle is operated or parked with a drive train using the clutch arrangement 101 in forward drive or reverse drive, wherein a gear can be engaged in a subsequent transmission as a parking lock. The electrical machine with the rotor 112 can be operated actively in the state a or can be switched off, the active state of the electrical machine being able to enter a torque to support the drive unit or to take up a torque from the drive unit in generator operation.

The second coupling state b is shown in Fig. 5b. The release mechanism 115 of the clutch arrangement 101 is displaced axially to such an extent that the plate spring tongues 162 are acted upon axially and the clutch 106 is disengaged. This is. The flywheel element 105 with the rotor 112 is uncoupled from the output shaft 108 . In this clutch state b, a gear change can be carried out in a subsequent manual transmission or the drive unit can be started in a direct start. It is also possible to charge the electrical energy store by means of driving the electrical machine by the drive unit.

Fig. 5c shows the clutch status c of the clutch assembly 101 in which both clutches 104 are open 106th The state c is switched from state b by further axial displacement of the release mechanism 115 in the direction of the drive shaft 103, the release mechanism 115 axially pressing and axially displacing the plate spring tongues 162 against a stop ring 169 of the clutch cover 161 , the one firmly connected to the clutch cover and itself also shifting pressure plate 130 opens the clutch 104 . In this state c, the flywheel element 105 continues to rotate with the angular momentum present before the clutch 104 is opened, with neglected friction. The rotational energy stored in the process can be used for the rotor 112 to generate electrical energy or the drive unit for a pulse start, the clutch 104 being closed again. In corresponding driving situations, it can also be used again for rolling on or moving the vehicle by closing the clutch 106 again. The impulse start and movement assistance by the flywheel element 105 can also be supported by the drive of the electric machine. Furthermore, when the flywheel mass element 105 is stationary, it is first possible to accelerate it by means of the electric machine with the rotor 112 .

The clutch state d of the clutch arrangement 101 , in which the clutch 104 is opened and the clutch 106 is closed, is set by means of a further axial displacement of the release mechanism 115 and thus the clutch cover 161 in the direction of the drive shaft 103 , the pressure plate 131 being pressed against the flywheel element 105 and the Clutch 106 is closed. The drive unit is decoupled from the rest of the drive train, so that in this state d the vehicle can only be operated electrically by means of the electric machine with the rotor 112 or the electric machine in generator mode kinetic energy fed into the drive wheels via the transmission or directly onto the output shaft Transforms energy, decelerating the vehicle. A return to the other driving modes c, b, a is direct through an axial displacement of the release in the opposite direction every day.

A clutch method for switching the clutch states a, b, c, d of the exemplary embodiment of a clutch arrangement 301 of the drive train according to the invention is described in FIGS. 6a-6d. The release mechanism 315 is supported by the release device - not shown in detail - in such a way that the release device 315 can be subjected to force in the event of an axial displacement in the pulling and pushing directions, for example by being hooked into a release device with an electric motor which is in both directions can be operated. The coupling states ad of FIGS. 6a-6d correspond to the states ad of FIGS. 5a-5d with regard to their use in the vehicle.

In clutch state a of FIG. 6a, the release mechanism 315 is in its position closest to the drive shaft 303 and presses the clutch 306 closed . The clutch 304 and the positive clutch 386 are also closed.

In state b of FIG. 6b, after an axial displacement away from the drive shaft 303 , the releaser 315 is in a state almost free of axial forces, in which the starting clutch 306 is opened and the separating clutch 304 is closed with the form-locking clutch 386 .

In state c of FIG. 6c, due to a further axial displacement of the release mechanism 315, the separating clutch 304 and the form-locking clutch 386 provided to support it are opened, so that the rotor 312 can rotate freely with the flywheel element 305 .

In FIG. 6d, after the disengagement 315 has been axially displaced into its position furthest away from the drive shaft 303 , the state d is shown, in which the clutches 304 , 386 as a jointly acting separating clutch are still open and the starting clutch 306 has been pulled again by the disengager 315 is.

The claims submitted with the application are drafted strikes without prejudice for obtaining further patent protection. The  The applicant reserves the right to add more, so far only in the description and / or To claim drawings disclosed combination of features.

Relationships used in subclaims point to further training the subject of the main claim by the features of the respective towards subclaim; they are not considered a waiver of achieving one independent, objective protection for the combinations of features of to understand related subclaims.

Since the subjects of the subclaims with regard to the prior art reserves the right to make its own independent inventions on the priority date Applicant before becoming the subject of independent claims or part to make statements of compliance. You can also continue to invent independently containing one of the subjects of the preceding subclaims have independent design.

The exemplary embodiments are not to be understood as a limitation of the invention hen. Rather, there are numerous variations within the scope of the present disclosure Rations and modifications possible, especially such variants, elements and combinations and / or materials, for example by combination or modification of individual in connection with that in the general Be  writing and embodiments and the claims described and in the features, elements or process contained in the drawings steps can be taken by the person skilled in the art with regard to the solution of the task are and through combinable features to a new item or lead to new process steps or process step sequences, also insofar as they Manufacturing, testing and working procedures concern.

Claims (73)

1.Drivetrain, in particular for motor vehicles, at least consisting of a drive unit, a flywheel element and a drive unit, the flywheel element being able to be coupled to the drive unit by means of a disconnect clutch and by means of a starting or shift clutch to the drive unit and the at least two clutches each egg nem open and closed clutch state can be actuated by means of a single release device with an axially displaceable release mechanism, characterized in that the clutch states of a clutch can be set independently of the clutch state of the other clutch. 2. Drive train, in particular according to claim 1, characterized in that at least one of the two clutches has a friction clutch with an axial by the release against an axially effective, the frictional engagement Energy storage shiftable pressure plate, an axially fixed Flywheel element with at least one friction engagement surface and one axially between frictional engagement surfaces of the pressure plate and the flywheel  can be brought into frictional engagement with friction linings and with the drive shaft or output shaft rotatably connected clutch disc is. 3. Drive train, in particular according to claim 1 and / or 2, characterized records that the actuation of the clutches to activate all the clutches conditions through a continuous axial displacement cycle of the off Rückers takes place. 4. Drive train, in particular according to one of the preceding claims, characterized in that the release system, manual or automatic is operated. 5. drive train, in particular according to one of the preceding claims, characterized in that the release system is hydraulic, pneumatic, operated electrically or as a combination of these. 6. drive train, in particular according to one of the preceding claims, that the disengaging device is arranged around the output shaft.   7. Drive train, in particular according to one of the preceding claims, characterized in that the axially displaceable releaser around the Ab drive shaft is arranged. 8. drive train, in particular according to one of the preceding claims, characterized in that by means of one of the clutches a drive unit like the internal combustion engine directly or indirectly with the output shaft is connectable. 9. drive train, in particular according to one of the preceding claims, characterized in that on the outer circumference of the flywheel mass a rotor of an electric machine is rotatably attached. 10. Drive train, in particular according to one of the preceding claims, characterized in that the separating clutch between the drive shaft and the flywheel element is effective. 11. Drive train, in particular according to one of the preceding claims, characterized in that the clutch between the swing mass element and the output shaft is effective.   12. Drive train, in particular according to one of the preceding claims, characterized in that the pressure plate of the clutch by means of Release lever against the axial action of the pressure plate of the switch coupling with the flywheel element to form the frictional connection bracing energy storage is axially displaceable and thus the switching clutch is actuated. 13. Drive train, in particular according to one of the preceding claims, characterized in that a ver with the pressure plate of the clutch bound clutch cover by means of the release against the axial we Kung a the pressure plate of the clutch with the flywheel ment to form the frictional locking energy storage is shiftable and thus the disconnect clutch is actuated. 14. Drive train, in particular according to one of the preceding claims, characterized in that the clutch by axial Beaufschla supply of radially inwardly oriented arms of the energy store how plate spring tongues of a plate spring are actuated by means of the release device. 15. drive train, in particular according to one of the preceding claims, characterized in that the separating clutch by axial loading  by means of radially inwardly oriented arms of the clutch cover of the releaser is operated. 16. Drive train, in particular according to one of the preceding claims, characterized in that the radially inward extension of the Clutch cover with axial interposition of the radially inward Lower arm of the energy storage of the clutch from the releaser be hit. 17. Drive train, in particular according to one of the preceding claims, characterized in that the radially inward extension of the Energy storage of the clutch axially through in the radially inward Further extensions of the clutch cover provided recesses to grab. 18. Drive train, in particular according to one of the preceding claims, characterized in that from an idle state of the release going in the direction of its axial displacement first the radially inward aligned boom of the energy storage of the clutch and there according to the radial inward extension of the clutch cover be charged.   19. Drive train, in particular according to one of the preceding claims, characterized in that when the clutch is axially displaced in The clutch is disengaged in the direction of the drive unit. 20. Drive train, in particular according to one of the preceding claims, characterized in that when the clutch is open, the separating clutch through axial displacement of the clutch housing towards the drive unit is opened using the release. 21. Drive train, in particular according to one of the preceding claims, characterized in that when the clutch and clutch are open with axial displacement of the clutch housing in the direction of the drive unit the clutch is closed. 22. Drive train, in particular according to one of the preceding claims, characterized in that the frictional engagement between the friction lining carrier, the pressure plate and the frictional engagement surface of the flywheel element Clutch with open clutch by means of a play of forces to Actuation of the pressure plates of the clutch and clutch seen energy storage takes place.   23. drive train, in particular according to one of the preceding claims, characterized in that the axial effective energy storage constant such as the spring constant of the axially effective energy store of the clutch taking into account the leverage ratio greater than that of the energy storage chers of the clutch. 24. Drive train, in particular according to one of the preceding claims, characterized in that the clutch cover means axially first kender and over the circumference through the flywheel element distributed stud bolt is connected to the pressure plate of the clutch. 25. drive train, in particular according to one of the preceding claims, characterized in that the stud bolts radially outside the pressure plate the clutch are arranged. 26. Drive train, in particular according to one of the preceding claims, characterized in that the stud bolts with the pressure plate and / or are screwed to the clutch cover. 27. Drive train, in particular according to one of the preceding claims, characterized in that the two pressure plates approximately on the are arranged the same extent.   28. Drive train, in particular according to one of the preceding claims, characterized in that at least one clutch with conical friction surfaces. 29. Drive train, in particular according to one of the preceding claims, characterized in that the separating clutch conically running Reibflä Chen, the smaller radius of the frusto-conical Reibflä Chen is aligned towards the drive unit. 30. Drive train, in particular according to one of the preceding claims, characterized in that to form at least one clutch at least one connected to the rotor and expanded radially inwards th flange part an axially fixed pressure plate is formed, the Pressure plate by means of an axially active energy store at a minimum least a contact surface for this forming, connected to the rotor Component supports and axially between the pressure plate and the pressure plate Clutch disc with friction linings is arranged. 31. Drive train, in particular according to one of the preceding claims, characterized in that that forming the at least one contact surface Component forms the contact surfaces for the energy storage of both clutches.   32. drive train, in particular according to one of the preceding claims, characterized in that the component is expanded radially inwards Flange part with two contact surfaces arranged on different circumferences Chen is and the energy storage depending on the position of the Releaser is supported on the radially outer or radially inner contact surface, wherein a bearing surface provided on the pressure plate radially between the two contact surfaces of the flange part is provided. 33. drive train, in particular according to one of the preceding claims, characterized in that the energy storage when the clutch is open in is arranged essentially stress-free and when actuated in each of the the pressure plate clamped against the pressure plate in the axial directions. 34. drive train, in particular close to one of the preceding claims, characterized in that the energy store depending on the axial position of the release two closed clutch states poses. 35. drive train, in particular according to one of the preceding claims, characterized in that the coupling with the two from the position of the  The clutch-dependent or disengaged clutch states Clutch is. 36. drive train, in particular according to one of the preceding claims, characterized in that the releaser to act on the two Couplings, one of the two couplings depending on the axial position of the release two closed clutch states has axially acts on a lever device, which from a lever system for axial application of energy to a clutch and Activation of the energy store to generate a first closed coupling state of a second clutch and a second lever system for generating the second closed clutch state of the second clutch exists. 37. drive train, in particular according to one of the preceding claims, characterized in that the separation designed as a friction clutch clutch is bridged by means of a positive coupling. 38. drive train, in particular according to one of the preceding claims, characterized in that the positive coupling by means of the lever direction, in particular by means of the lever system that the to be bridged Coupling operated, is coupled.   39. drive train, in particular according to one of the preceding claims, characterized in that the positive coupling and the separating clutch separate the drive unit from the flywheel element. 40. drive train, in particular according to one of the preceding claims, characterized in that the positive coupling during an axial releaser after opening the clutch and before opening the friction clutch is disengaged. 41. drive train, in particular according to one of the preceding claims, characterized in that the lever systems axially against each other are available. 42. drive train, in particular according to one of the preceding claims, characterized in that starting from a basic state at ge engaged clutches first when the clutch is axially displaced actuated the first lever system and the clutch with the two closed Clutch states opens, with the first lever system on the second Lever system axially and the second lever system is not shifted axially.   43. drive train, in particular according to one of the preceding claims, characterized in that both lever systems via at least one have axial stop, which is non-positively in the axial direction on the lever Actuation of the energy storage acts. 44. drive train, in particular according to one of the preceding claims, characterized in that by means of one of the two stops both Ener be charged. 45. drive train, in particular according to one of the preceding claims, characterized in that one of the two energy storage under Zwi Activation of a translation to extend the release path from the attack is applied. 46. drive train, in particular according to one of the preceding claims, characterized in that the translation of two radially inward he further flange parts, which are axially non-positively connected are, the first flange part in the axially active energy storage pressure plate loaded by him and the second flange part rests against the stop.   47. drive train, in particular according to one of the preceding claims, characterized in that the axial connection of the flange parts at the Inner circumference is provided. 48. drive train, in particular according to one of the preceding claims, characterized in that the provision of the flange parts by means of a further axially effective energy storage takes place. 49. drive train, in particular according to one of the preceding claims, characterized in that the flywheel element on the drive shaft or a component firmly connected to it is rotatably mounted. 50. drive train, in particular according to one of the preceding claims, characterized in that the rotor on the drive shaft or with a the drive shaft fixed component is rotatably mounted. 51. drive train, in particular according to one of the preceding claims, characterized in that the component is connected to the drive shaft ner flange is.   52. drive train, in particular according to one of the preceding claims, characterized in that the pressure plate or the rotor radially except half of the flange's screw connections to the drive unit. 53. drive train, in particular according to one of the preceding claims, characterized in that the flange the clutch disc with the Friction linings for the separating clutch rotatably. 54. drive train, in particular according to one of the preceding claims, characterized in that in the force path between the drive shaft and the Output shaft a torsional vibration damper is provided. 55. drive train, in particular according to one of the preceding claims, characterized in that the torsional vibration damper in the power flow is provided between the starting clutch and the drive train. 56. drive train, in particular according to one of the preceding claims, characterized in that the torsional vibration damper in the clutch is provided with the friction linings.   57. drive train, in particular according to one of the preceding claims, characterized in that the torsional vibration damper in the force path is provided between the drive shaft and the starting clutch. 58. drive train, in particular according to one of the preceding claims, characterized in that the torsional vibration damper is a split Flywheel, at least consisting of two against the effect of in Effective energy storage circumferentially relatively rotatable Inertia is. 59. drive train, in particular according to one of the preceding claims, characterized in that one of the flywheel masses the flywheel element or the rotor. 60. drive train, in particular according to one of the preceding claims, characterized in that the split flywheel is a primary with the Drive shaft has a fixed flywheel mass, which counter to the Effect of energy storage against a rotatably mounted on it secondary flywheel is relatively rotatable, the flywheel senelement or the rotor of the secondary flywheel by means of the separation clutch is switchable.   61. drive train, in particular according to one of the preceding claims, characterized in that flywheel element or rotor and se separate flywheel mass separately on one with the drive shaft firmly connected flange are stored. 62. drive train, in particular according to one of the preceding claims, characterized in that the clutch disc of the disconnect clutch is fixed with a disk part connected to the secondary flywheel is bound. 63. drive train, in particular according to one of the preceding claims, characterized in that the energy storage of the divided flywheel are arranged approximately at the same radial height as the rotor. 64. drive train, in particular according to one of the preceding claims, characterized in that the double clutch for at least one clutch development with a device to compensate for wear of the friction linings is permitted. 65. drive train, in particular according to one of the preceding claims, characterized in that the wear compensation device for both Couplings is effective.   66. Method for actuating a drive train, at least consisting of two units which can be connected to a shaft by means of at least two clutches, in particular for motor vehicles, with a disengagement device, clutch states of a first and a second clutch being disengaged with an axially displaceable device Releasers are actuated and the clutch states with the release device

• a) first clutch closed, second clutch closed,
• b) first clutch closed, second clutch opened,
• c) first clutch opened, second clutch opened,
• d) first clutch open, second clutch closed

are switchable. 67. The method, in particular according to claim 66, that the clutch states are sequential in the order

• a) first clutch closed, second clutch closed,
• b) first clutch closed, second clutch opened,
• c) first clutch opened, second clutch opened,
• d) first clutch open, second clutch closed

be switched. 68. The method, in particular according to claim 67, that the clutch states are sequential in the order

• a) first clutch closed, second clutch closed,
• b) first clutch closed, second clutch opened,
• c) first clutch opened, second clutch opened,
• d) first clutch open, second clutch closed

can be switched by means of an axially continuous forward and backward movement of the releaser. 69. The method, in particular according to claim 66 and / or 67, characterized thereby records that the first clutch is a separating clutch, the two Ag gregate couples with each other and the second clutch an on is the drive clutch, which the aggregates depending on the clutch condition the separating clutch couples to an output shaft. 70. The method, in particular according to one of the preceding claims, characterized characterized in that the two units an internal combustion engine and a Are electric machine. 71. The method, in particular according to one of the preceding claims, characterized characterized by a starting point at which both clutches  are closed, the actuation of the clutches in one direction the axial effect of at least one energy storage takes place. 72. Method, in particular according to one of the preceding claims, thereby characterized in that the actuation of the clutches by pulling or pushing releaser. 73. Powertrain with a feature disclosed in the application documents.