JP2008137650A - Power transmission device, power train equipped with power transmission device, and method for controlling operation mode of power transmission device provided at power train - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide configuration space-saving to the utmost having possibility of optimization of a regenerative braking process and minimization of idling loss particularly when used for a hybrid driving device comprising an electric machine operable as a power train, particularly at least as a generator. <P>SOLUTION: This power transmission device 1 has a switchable clutch device 10 for separating a turbine wheel T from an output body 3. The clutch device 10 is arranged in series to the turbine wheel T and in parallel to devices 7, 8 for by-passing an output transmission line through a hydrodynamic component 4 viewed in a power transmitting direction between an input body 2 and the output body 3. A vibration damping device 14 and the devices 7, 8 for by-passing the output transmission line through the hydrodynamic component 4 are arranged in series. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The invention relates to a multi-function unit for use in a powertrain with a power transmission device, in particular a hybrid drive device having at least one electric machine operable as a generator, comprising at least one input body and an output body And a hydrodynamic component disposed between the input body and the output body, the hydrodynamic component including at least one pump wheel, a turbine wheel, and a hydrodynamic component The present invention relates to a type having a device for bypassing the output transmission path through the components and a device for damping vibration.

  Furthermore, the invention relates to a power train for use in particular in vehicles.

  The invention further relates to a method for controlling the operating mode of a force transmission device of the type described above provided in a power train of the type described above.

  The force transmission device arranged between the prime mover and the transmission component unit is known on the basis of the known prior art in a number of configurations. This known force transmission device generally has one input body and at least one output body. In this case, the input body is connectable to a prime mover, generally an internal combustion engine, at least indirectly, ie directly or via another transmission element, and at least one output body is connected to the force transmission device. It is connected to the installed transmission component unit, generally a change gear box. Hydrodynamic components in the form of a hydrodynamic speed / torque converter are preferably arranged between the input body and the output body. The hydrodynamic rotation / torque converter has at least one pump wheel, one turbine wheel, and at least one stator. In order to bypass the hydrodynamic output transmission path, a device called a lock-up clutch is provided. The device has a first clutch member and a second clutch member. Both clutch members can be operatively coupled to each other at least indirectly. In this case, the lockup clutch serves for the connection between the input body or the coupling between the input body and the pump wheel and the turbine wheel. Activation or deactivation is performed via an adjustment device. This adjustment device is in the simplest case formed in the form of a piston element which can be operated by a pressure medium. Depending on the configuration, the entire hydrodynamic speed / torque converter or force transmission device is formed as a two-pass unit or a three-pass unit. In this case, in the three-passage structure, the adjusting device for the lock-up clutch is loaded with a pressure that can be adjusted separately. The hydrodynamic speed / torque converter is adapted to the application of a ratio to the connecting portion arranged corresponding to the working chamber and the inner chamber surrounded by the housing and the hydrodynamic speed / torque converter. Flowed in the heart direction or in the centrifugal direction.

  In connection with the connection between the connection and the pressure medium supply system, it is possible to form a circuit existing outside the flow circuit generated in the hydrodynamic speed / torque converter during operation. In this case, the output is transmitted purely hydrodynamically within a predetermined operating range by means of force transmission between the input body and the output body via hydrodynamic components. The primary wheel that functions as a pump wheel is directly connected to the prime mover, and the turbine wheel is connected to an output body or an input body of a rear-mounted change gear box. Especially when used in vehicles, the hydrodynamic output transmission has a drawback that occurs when a relatively high speed / moment adjustment is required in the driving characteristics map of the prime mover, ie 2-3% slip due to the principle. In order to avoid deductions and characteristic deductions, the lock-up clutch is actuated and the output is transmitted between the input body and output body of the force transmission device, bypassing the mechanically hydrodynamic output branch. The

  The braking process is advantageously carried out electrically, in combination with a hybrid drive that stores braking output when using an electric machine that can be operated as a generator, followed by a force transmission device, into the transmission or into the transmission When the electric machine is placed in front of the machine, the remaining moment is still input to the transmission or the prime mover is dragged in the braking operation when the lockup clutch is released, so that the total braking output is converted into an electrical output. Can't store.

Further, during idling of the prime mover, the prime mover can be separated from the output body by releasing the lock-up clutch. However, torque is still introduced into hydrodynamic components. This torque is also introduced into the transmission based on the connection with the rear transmission. On the other hand, torque impact is introduced into the hydrodynamic components from the driven device side. Therefore, in order to separate the prime mover from the transmission, idling stops in the transmission, i.e., the interruption of the force transmission path during idling in the transmission, have been proposed or described in U.S. Pat. No. 5,020,646. As shown in the figure, a clutch device is provided for separating the pump wheel from the transmission component unit disposed behind the force transmission device and thus for separating the prime mover. In this case, a pump wheel clutch is only required for this operating range. Pump wheel clutches are often also arranged in areas that lead to an increase in the required construction space in the radial or axial direction. A housing must be provided between the pump wheel and the prime mover, generally based on the separability between the pump wheel and the input body of the force transmission device. This housing also encloses all units, in particular the pump wheel shell. However, the hydrodynamic components remain functionally associated with the transmission component unit when the pump wheel is separated, i.e., connected to the transmission component unit. This leads to drag loss particularly in the fuel supply shutoff operation during separation. The idling stop in the transmission certainly cuts off the force transmission path, but the hydrodynamic components are still connected to the prime mover, so that moments are introduced into the transmission at least up to the point of separation. Is done. This appears in the form of drag losses.
US Pat. No. 5,020,646

  The object of the present invention is therefore to improve a force transmission device of the type mentioned at the outset, avoiding the drawbacks mentioned above, in particular to a power train, in particular a hybrid drive device comprising an electric machine operable as a generator. The aim is to provide a space saving configuration as much as possible with the possibility of optimizing the regenerative braking process in use and minimizing idle losses. It is desirable that the solution according to the invention is characterized by a short structure and a small number of components.

  In order to solve this problem, in the force transmission device of the present invention, the force transmission device has a switchable clutch device for separating the turbine wheel from the output body, and the clutch device is connected to the input body. Seen in the direction of force transmission to and from the output body, it is arranged in series with the turbine wheel and in parallel with the device for bypassing the output transmission path via the hydrodynamic component. The device for attenuating the noise and the device for bypassing the output transmission path via the hydrodynamic component are arranged in series.

  According to an advantageous configuration of the force transmission device of the invention, the device for damping the vibration is arranged in parallel with the clutch device.

  According to an advantageous configuration of the force transmission device according to the invention, the device for damping the vibration is a device for bypassing the output transmission path via the hydrodynamic component, and from the input body to the output body. Seen in the direction of force transmission.

  According to an advantageous configuration of the force transmission device of the invention, the element of the device for bypassing the output transmission path via the hydrodynamic component is a component of the device for damping vibrations.

  According to an advantageous configuration of the force transmission device according to the invention, the element of the clutch device is a component of the device for damping vibrations.

  According to an advantageous configuration of the force transmission device of the present invention, the device for bypassing the output transmission path via the hydrodynamic component has a lock-up clutch, which It is formed as a connective clutch, which has at least one first clutch member and a second clutch member, both of which can be operatively coupled to each other via an adjusting device. is there.

  According to an advantageous configuration of the force transmission device of the invention, the adjustment device and the second clutch member are formed by one component.

  According to an advantageous configuration of the force transmission device of the invention, the connection between the input body and the pump wheel is formed by a housing rotating together, the first clutch member being a housing It is formed by a partial region.

  According to an advantageous configuration of the force transmission device of the invention, the switchable clutch device for separating the turbine wheel is formed as a frictionally connected clutch, the clutch being connected to the first clutch member and the first clutch member. Two clutch members, and both clutch members can be coupled to each other via the adjusting device.

  According to an advantageous configuration of the force transmission device according to the invention, each adjusting device has a piston element that can be loaded with a pressure medium, the piston element being pressure / liquid tightly connected to an input body, an output body or A chamber that can be loaded with a pressure medium or a control medium is formed on the elements of the turbine wheel and the clutch device, and is supported so as to be movable in the axial direction.

  According to an advantageous configuration of the force transmission device of the invention, the device for damping vibration comprises a primary member and at least one secondary member, both members being arranged coaxially with each other. Thus, they are restricted in the circumferential direction and are rotatable relative to each other, and are connected to each other via a means for torque transmission and a means for damping connection.

  According to an advantageous configuration of the force transmission device of the invention, the means for torque transmission and / or the means for the damping connection comprise a spring unit, which comprises a primary member and a secondary member. And is supported by.

  According to an advantageous configuration of the force transmission device of the invention, the device for damping vibrations is formed as a hydraulic damper, which has a damping chamber that can be filled with a hydraulic liquid. , As a means for damping connection.

  According to an advantageous configuration of the force transmission device of the invention, the primary member of the device for damping vibrations is formed by the piston element of the device for bypassing the output transmission path via the hydrodynamic component. It has become so.

  According to an advantageous configuration of the force transmission device of the present invention, the secondary member is formed as a pot-shaped molded member that forms a notch oriented in the axial direction, and the axial extension of the molded member. A switchable clutch device is disposed within the length.

  According to an advantageous configuration of the force transmission device of the invention, the first clutch member of the switchable clutch device for separating the turbine wheel is coupled to the turbine wheel in a non-rotatable manner. The clutch member is coupled to the secondary member of the device for damping vibration so as not to rotate relative to each other, and both clutch members have a friction plate assembly including a friction plate support, The body is coupled to the connecting element in a non-rotatable manner by forming an axial stopper, the adjusting device has a piston element, which is in the region of its outer peripheral surface Guided by the friction plate support, it partitions a pressure chamber that can be loaded with a pressure medium.

  According to an advantageous configuration of the force transmission device according to the invention, the hydrodynamic component is formed as a hydrodynamic speed / torque converter, in particular as a three-element one-stage two-phase converter, A stator is provided, and the stator is supported by a stationary or rotating element via a one-way clutch.

  According to an advantageous configuration of the force transmission device according to the invention, the hydrodynamic component is formed as a hydrodynamic clutch.

  According to an advantageous configuration of the force transmission device according to the invention, the pump wheel is connected to the pump wheel shell in a non-rotatable manner, the pump wheel shell in the axial direction and in the radial direction with respect to the turbine wheel. An intermediate chamber is formed for accommodating another element of the force transmission device, and the pump wheel shell is a component of the housing of the force transmission device.

  According to an advantageous configuration of the force transmission device of the present invention, an operating medium supply / guidance system is arranged correspondingly to the force transmission device, and the operating medium supply / guidance system is connected to the hydrostatic device via the first connecting portion. Connected to the working chamber of the dynamic component, connected to the inner chamber via a second connection in the region of the temporarily formed chamber capable of being loaded with a pressure medium, Via a connection part, it is connected to a chamber arranged corresponding to the adjusting device of the clutch device that can be loaded with a pressure medium and can be switched.

  Furthermore, in order to solve the above-described problems, the power train of the present invention is provided with a first prime mover, which is provided via the force transmission device according to any one of claims 1 to 20. An electric machine that can be connected to the output transmission unit and can be operated as at least a generator is provided, and the electric machine is disposed behind the switchable clutch device.

  According to an advantageous configuration of the power train of the invention, the electric machine is arranged coaxially with respect to the power train.

  Furthermore, in order to solve the above-mentioned problems, the method according to the present invention provides an output transmission path via a hydrodynamic component when setting a target value, a delay and / or a prescribed braking moment after a change in travel speed. A device for bypassing an output transmission path through a hydrodynamic component during operation and a switchable clutch device. Dissociated and related to the target value, the electric machine was controlled to generate a braking moment.

  The force transmission device has one input body and at least one output body. In this case, the input body is connectable to the prime mover at least indirectly, and at least one output body is connectable to a rear transmission unit, for example, a rear transmission input body. Thus, the output body is often also formed directly by the transmission input shaft. A hydrodynamic component having at least one primary wheel that functions as a pump wheel and one secondary wheel that functions as a turbine wheel is disposed between the input body and the output body. This hydrodynamic component forms a working chamber that can be filled or filled with the operating medium. A corresponding flow circuit is created in the working chamber when power is transmitted through hydrodynamic components. When configured as a hydrodynamic rotation / torque converter, at least one further stator is provided. The stator is supported by a stationary element or a rotating element via a one-way clutch. In order to bypass the hydrodynamic output transmission path, a device for bypassing the output transmission path via the hydrodynamic component is arranged corresponding to the hydrodynamic component. This device is generally formed as a lock-up clutch and has at least one first clutch member and one second clutch member. Both clutch members can be operatively connected to each other. According to the present invention, there is provided a clutch device that is placed behind the turbine wheel in parallel with the lock-up clutch when viewed in the direction of force transmission from the input body to the output body. In this case, this clutch device, which can also be called a turbine wheel clutch, serves to separate the hydrodynamic components from the output body or the remaining power train that can be connected to the output body and the prime mover. Upon simultaneous release of the lock-up clutch, the force transmission device can be completely disconnected from the force transmission. This makes it possible to avoid idling losses due to the entrainment of the hydrodynamic component elements and the circulation of the flow medium in the working chamber. The clutch device can be switched. The pump wheel further drives the turbine based on the possibility of selective disconnection of the output transmission path by switching the clutch device. In this case, the stator rotates together. This is because the pump wheel and the turbine wheel have substantially the same rotational speed. However, the moment is not continuously guided to the rear transmission because of the clutch device released in this operating state. Furthermore, even in the case of braking, the drag moment can no longer be input to the prime mover.

  Advantageously, the force transmission device is a so-called “pump wheel clutch”, i.e. provided between the input body and the pump wheel, selectively connecting the pump wheel to the input body or connecting the pump wheel to the input body. Does not have a clutch to separate from.

  It is advantageous to stop the hydrodynamic components. In this case, this stop no longer transmits moments due to lack of support. Depending on the arrangement type and operation, the clutch device can assume the function of a pure separating clutch for separating the prime mover and the transmission. The connectability and the lack of separation at the connection between the pump wheel and the input body allow the use of the pump wheel shell as a housing member that rotates together, thereby allowing a separate housing surrounding the entire unit. It can be made unnecessary.

  The hydrodynamic component is preferably a hydrodynamic speed / torque converter. This hydrodynamic speed / torque converter is generally always filled with a medium, so even if hydrodynamic power transmission is not performed, the operating medium is connected to the hydrodynamic type via an external circuit. The rotation speed / torque converter can be carried out and returned to the working chamber of the hydrodynamic rotation speed / torque converter. Based on the always applied filling, generally full filling (however, a corresponding partial filling condition is also possible), the operating medium is always circulated together during idling operation and the corresponding loss output Leads to a proportion. Based on the rearward placement of the turbine wheel, the possibility according to the invention to completely separate the hydrodynamic components from the driven device behind the force transmission device allows the hybrid drive, i.e. alternative Or, when braking in a powertrain with an additional electric machine as an additional drive unit and when using the electric machine while the generator is operating as a braking device, the drag loss by the prime mover can be avoided and the total braking output Can be generated entirely through an electric machine operable as a generator, converted into electrical energy and stored in an energy storage device. Furthermore, this configuration makes it possible to avoid a moment input in the transmission unit placed behind the force transmission device during idling.

  Both clutch devices, i.e. the device for direct coupling and the turbine wheel clutch, can be connected in series or in parallel. The operations of both clutch devices may be performed separately in a controllable manner, or may be performed at least forcibly connected to at least one operating state. Depending on the arrangement type, connection and operation of the individual clutch devices, the force transmission device can perform different functions. The advantage is that the clutch device does not have to be operated during traction operation when the lockup clutch is engaged. Therefore, the clutch device need only be designed for the moment that it wishes to transmit to the maximum via hydrodynamic components and can be dimensioned accordingly. The required cooling output for the clutch device is less.

  During the idling / braking operation, the lockup clutch and the clutch device are disconnected. This makes it possible to stop the hydrodynamic components and to completely separate the prime mover connected to the input body of the force transmission device from the transmission unit placed behind the force transmission device.

  According to a particularly advantageous configuration, the device for damping the vibration is arranged in parallel with the clutch device and in series with the lock-up clutch. In this case, here, this arrangement may be performed between the input body and the output body as viewed in the direction of force transmission, either in front of or behind the lock-up clutch. This configuration is at least generally equivalent to the main working range of the respective field of use and, in the operating range without hydrodynamic power transmission, vibration damping is assured to the desired degree. When transmitting power through hydrodynamic components, the advantage is that the device for damping the vibrations acts at least as a damper.

  With regard to the structural configuration, the solution according to the invention is characterized by a high degree of functional concentration. In this case, according to the first configuration, the device for bypassing the output transmission path in the hydrodynamic output branching unit has at least one first clutch member and one second clutch member. ing. Both clutch members can be operatively coupled to each other at least indirectly, ie directly or via another transmission element. The first clutch member and the second clutch member are preferably formed as disk elements. In this case, the working connection is obtained via a controllable adjustment device. According to a first advantageous configuration, at least one clutch member, preferably the first clutch member, is formed directly by the housing. According to another advantageous configuration, the second clutch member is additionally or alternatively formed by the adjusting device, in particular the piston element itself. This enables a lock-up clutch having a structure that is extremely short in the axial direction. Furthermore, based on the possible size of the provided surface area in the housing, the required transmittable moment can be transmitted only by the friction surface pair. For this purpose, a substantially axially oriented surface area in the housing and the piston element is used.

  Another functional concentration that is theoretically possible is possible between the clutch device, in particular the lock-up clutch, and the device for damping the vibration. The device for attenuating this vibration has a primary member that functions as an input member and a secondary member that functions as an output member. Both members are relatively limited and can rotate in the circumferential direction, and are arranged coaxially with each other. The primary member and the secondary member are connected to each other via a means for torque transmission and a means for damping connection. Advantageously, the means for torque transmission are formed by means for a damping connection. In the simplest case, the means for torque transmission and the means for damping connection are formed in the form of a spring unit.

  According to a particularly advantageous refinement, the adjusting element, in particular the piston element of the device for directly connecting the hydrodynamic output branch, functions simultaneously as the primary member. In this case, the second clutch member of the lock-up clutch is simultaneously a component or a component of the primary member of the device for damping the vibration.

  The aforementioned combinatorial possibilities and functional concentrations in the individual component elements can be used separately or in combination with one another.

  The switchable clutch device is arranged between the turbine wheel and the output body of the force transmission device, particularly the secondary member. In this case, the coupling is advantageously arranged in such a way that the switchable clutch device is axially within the extension length of the device for damping the vibrations in terms of space, Furthermore, in the radial direction, it is carried out so as to be arranged inside the device for damping vibrations. In this case, the secondary member of the device for damping this vibration is correspondingly shaped in the radial direction, so that the secondary member has a so-called pot-like notch in the axial direction. . A switchable clutch device can be incorporated in the notch. In order to be able to load the adjusting device of the switchable clutch device with a pressure medium, a pressure chamber is arranged corresponding to the adjusting device. This pressure chamber is partitioned by a piston element and a turbine wheel. In this case, an individual clutch member, preferably a first clutch member, which is non-rotatably coupled to the turbine wheel, is coupled to the turbine wheel in material connection, whereby the pressure chamber Pressure and liquid-tight configuration.

  For the operation medium supply, an operation medium supply system and / or a guidance system is provided. This operating medium supply system and / or guidance system can be formed in different ways, and in the simplest case has an operating medium supply source. The operating medium supply source is connected to connections provided in individual pressure chambers for operating the switchable clutch device, the lock-up clutch, and the hydrodynamic components.

  The supply is advantageously effected via the configuration of the connecting element as a hollow shaft, whereby individual conduits can here be guided coaxially with one another.

  In all configurations, a corresponding adjusting device is arranged corresponding to the lock-up clutch and the clutch device. This adjustment device is in the simplest case formed as a piston element. In the case of a configuration in a disk structure or a multi-plate structure, the adjusting device is effective in elements that can be coupled to each other. In this case, each individual adjustment device can advantageously be controlled separately. This controllability is ensured by the configuration of the force transmission device in a multi-passage structure. For this purpose, at least one first connection passage and one second connection part are provided. The first connection passage is connected at least indirectly to the working chamber filled with the operating medium. The second connection is between the outer peripheral surface of the hydrodynamic component and the inner peripheral surface of the housing or, advantageously, the so-called “pump wheel shell”, which is non-rotatably coupled to the pump wheel. Connected to the interior room. This pressure in the intermediate chamber loads the adjusting device between the lock-up clutch and the clutch device, in particular for connection. For the release, a separate chamber capable of being loaded with a pressure medium is correspondingly arranged in each adjusting device. In this case, the pressure-bonding force of the adjusting device can be adjusted via a pressure difference between each chamber that can be loaded with a pressure medium and the inner chamber. In this case, the chamber which can be loaded with a pressure medium, arranged correspondingly to the adjusting device, consists of the adjusting device, the wall of the connecting element, in particular the output body of the force transmission device, and one element of the lock-up clutch, preferably the first 1 clutch member or an adjusting device and a turbine wheel. For this purpose, the adjusting device, in particular the piston element, is guided by the connecting element in a pressure- and liquid-tight manner. The connection element of the lockup clutch to the chamber that can be loaded with a pressure medium is generally an output body of the force transmission device, in particular, an element connected to the output body in a non-rotatable manner and a relative number of rotations relative to the output body A rotatable element, generally a housing. This applies analogously to clutch devices. The piston element is advantageously supported axially and pressure / liquid tightly by the turbine wheel and one element of the clutch device. The arrangement of the piston element and the other element of the force transmission device can be carried out such that the operating directions are opposite or directed in the same direction. The intermediate chamber thus formed can be arbitrarily loaded with a pressure medium and is advantageously carried out with a controlled load.

  The arrangement of the lock-up clutch, the clutch device and the device for damping the vibrations is advantageous with respect to the two elements coaxially with each other or coaxially with the rotational axis of the force transmission device and in the axial direction Is carried out in one plane or slightly offset from each other. In this case, the clutch device is advantageously arranged with a smaller diameter than the lock-up clutch, and both clutch devices are arranged with a shift in the axial direction. The arrangement of the device for damping the vibrations is preferably performed between both clutch devices. In this case, the clutch device for separating the turbine wheels is advantageously arranged within the axially extended length of the device for damping the vibrations.

  In the following, the best mode for carrying out the present invention will be described in detail with reference to the drawings.

  FIG. 1 shows a simple outline of the basic structure and basic principle of a power transmission device 1 formed according to the invention with turbine wheel separation used in a power train 41, in particular a vehicle power train with a hybrid drive. It is shown in the figure. The force transmission device 1 has at least one input body 2 and an output body 3. In this case, the input body 2 is preferably connectable to a prime mover 11 in the form of an internal combustion engine. The output body 3 is coupled to the transmission input shaft 43 of the transmission 42 that is placed behind the force transmission device 1 so as not to be relatively rotatable, or forms a transmission input shaft. A hydrodynamic component 4 in the form of a hydrodynamic speed / torque converter 5 is preferably arranged between the input body 2 and the output body 3. The hydrodynamic rotational speed / torque converter 5 is connected to the transmission input shaft 2 or the output body 3 from the input body 2 through the coupling as seen in the traction operation during output transmission when used in a vehicle. A primary impeller that can be coupled to the input body 2 including the prime mover 11 so as not to rotate relative to the input body 2 and functions as a pump wheel P, and another second wheel that can be at least indirectly connected to the output body 3 and functions as a turbine wheel T. Impeller and at least one stator L. In this case, the hydrodynamic rotational speed / torque converter 5 functions to simultaneously convert torque and rotational speed, and is generally filled with the operating medium in all operating states. As a result, output transmission via the hydrodynamic component 4 is performed via the first output branch 6 in the first operating state. The first output branch section 6 is also called a hydrodynamic output branch section. In order to bypass the output transmission path via the hydrodynamic component 4, a device 7 for directly connecting the hydrodynamic component 4 is provided. This device 7 is formed as a so-called “lock-up clutch 8” and is preferably formed in a disc structure, in particular a multi-plate structure, as a switchable frictionally connected clutch. The device 7 works in the second output branch 9 to bypass the output transmission via the hydrodynamic component 4. For this purpose, the lock-up clutch 8 is arranged between the input body 2 and the output body 3 and connects the input body 2 and the output body 3 at least indirectly to each other.

  The force transmission device 1 can be incorporated in the power train 41 between the prime mover 11 and the transmission 42, here, the transmission input shaft 43. The force transmission device 1 is placed in front of the transmission 42. The transmission 42 is formed, for example, as a change gear box, particularly as a shift gear box. For this purpose, the output body 3 of the force transmission device 1 can be coupled to the input body 43 of the transmission 42, preferably it is coupled or forms the input body 43 and thus the transmission input shaft. It is preferably arranged coaxially or eccentrically, i.e. in parallel, connected to the power train 41 in the transmission 42 or between the transmission 42 and the force transmission device 1 or in the force transmission device 1. In the case of use in a hybrid drive device with at least an electric machine EM operable as a generator, the braking process via the electric machine EM operable in this case as a generator due to the torque released from the prime mover 11 In order to avoid superposition or drag of the prime mover 11 and to generate the full braking output via the electric machine EM, a device for separating (disconnecting) the turbine wheel T from the power train 41, in particular a switchable clutch device 10 Between the hydrodynamic component 4 and the transmission input shaft 43, particularly the output body 3. It is provided between the wheel T and the output member 3. In this case, the arrangement is performed after the turbine wheel T as viewed in the direction of force transmission from the input body 2 to the output body 3. Depending on the switchability between the lock-up clutch 8 and the switchable clutch device 10 in the form of a device for separating the turbine wheel T from the power train 41, variously depending on this device or configuration of the force transmission device 1. Different functions can be realized. The first function is to transmit the output from the input body 2 to a driven device connected at least indirectly to the output body 3 via a first output branch 6 in a hydrodynamic manner or hydrodynamic. Bypassing the hydraulic component 4, in particular the hydrodynamic speed / torque converter 5, is transmitted via the second output branch 9 by switching the lockup clutch 8 or the turbine wheel T is driven. In particular, by separating from the output body 3 and thus from another transmission element connected at least indirectly to the output body 3, the transmission unit, in particular a gearshift, placed behind the force transmission device 1 with the lock-up clutch 8 open. It is to enable separation of the prime mover 11 from the machine 42. Furthermore, the force transmission device 1 advantageously has a device 14 for damping vibrations, in particular in the form of a torsion damper or a torsional vibration damper. In this case, the arrangement can be done in different ways. According to a particularly advantageous configuration, the device for dampening vibrations is placed behind the lock-up clutch 8 as viewed in the output transmission path, and furthermore only at the output body of the device for dampening vibrations, It is not connectable to the switchable clutch device 10 for turbine wheel separation. A device 14 for damping vibration is arranged in parallel with the clutch device 10 and in series with the lock-up clutch 8. In this case, the device 14 for damping the vibration is only effective in a directly connected operation, ie mechanical transmission of power from the prime mover 11 to the output body 3. At the time of output transmission in hydrodynamic operation, the device 14 for damping vibration is only effective as a vibration damper.

  There are many possibilities for the specific configuration of the device 14 to damp vibrations. These possibilities differ in particular with regard to the type of damping connection used and the connection for torque transmission. The device 14 for damping vibration functions as an elastic clutch in the output transmission path from the input body 2 to the output body 3 via the lock-up clutch 8, that is, transmits torque. The device 14 for damping vibration has a primary member 15 called an input member and a secondary member 16 called an output member when viewed in this output transmission direction. In this case, the primary member 15 and the secondary member 16 are arranged coaxially with each other, and can be rotated while being relatively limited to each other in the circumferential direction. The connection between the primary member 15 and the secondary member 16 is made via means 17 for torque transmission and means 18 for damping connection. In this case, the means 17 for torque transmission and the means 18 for damping connection may be formed by the same component. Advantageously, torque transmission is realized via an energy storage unit 19 in the form of a spring unit 20. This energy storage unit 19 simultaneously functions as a means 18 for the damping connection. Other configurations are possible, particularly if damping action via additional friction points or another damping concept, for example hydraulic damping, is realized.

  Further, in the configuration shown in FIG. 1, for example, a device 47 for damping vibration is provided between the prime mover 11 and the force transmission device 1 in the power train.

  According to the basic concept described in FIG. 1, in part by the simultaneous or slightly time-shifted release of the lock-up clutch 8 and the switchable clutch device 10 for separating the turbine wheel T, The prime mover 11 is separated from the transmission component unit 42 or the rest of the power train after the force transmission device 1 and thus comprises a regenerative braking device via an electric machine EM that can be operated at least as a generator. In the case of the hybrid drive system, in this case, the braking output supplied through the wheel via the power train 41, particularly when used in a vehicle, is converted into electrical energy and temporarily stored in the energy accumulator 44. Can be stored and / or used as drive energy for the accessory. Both clutch devices 8, 10 remain separated during the braking process.

  FIG. 2 shows an axial sectional view of the force transmission device 1 in series with a device 14 for damping vibration and a switchable lockup clutch 8 and switchable for the purpose of turbine wheel separation. A particularly advantageous structural configuration of the coupling structure described in FIG. 1 with a parallel connection to the clutch device 10 is shown. This configuration is characterized by an arrangement that is very short in the axial direction and is particularly space-saving. In this case, as seen in the direction of force transmission between the input body 2 and the output body 3, the lockup clutch 8, the device 14 for damping the vibration, and the switchable clutch device 10 for separating the turbine wheel, The hydrodynamic component 4 is arranged. Advantageously, here, in order to obtain a particularly compact construction, the lock-up clutch 8 is integrated together in a device 14 for damping vibrations, and a switchable clutch device 10 is provided in the radial direction. , Between the device 14 and the turbine wheel T within the extension length of the device 14 for damping vibrations. The hydrodynamic component 4, in particular the pump wheel P of the hydrodynamic speed / torque converter 5, has a pump wheel shell 12. The pump wheel shell 12 is connected to the pump wheel P so as not to rotate relative to the pump wheel P, or forms an integral unit with the pump wheel P, so that the turbine wheel T is at least partially in the circumferential direction in the axial direction. Forming and surrounding. The pump wheel shell 12 is directly connected to or forms the input body 2. Advantageously, the connection is made via a housing member 45.2. The housing member 45.2 is formed in a bell shape, and the inner chamber 21 as the housing 45 together with the pump wheel shell 12 as another housing member 45.1 is connected to the hydrodynamic rotation speed / torque converter 5 and The switchable clutch device 10, the device 14 for damping vibrations, and the lockup clutch 8 are housed and formed.

  The specific structural configuration shown in FIG. 2 is characterized by a high functional concentration. This functional concentration is achieved by the fact that individual components and components are used in multiple, that is, the individual components and components have functions in different configuration units. The lock-up clutch 8 is here preferably configured as a disk clutch, and a first clutch member 8.1 in the form of a disk element 22.1 and a second clutch also in the form of a disk element 22.2. And a clutch member 8.2. The friction surface areas 24.1, 24.2 formed in the two clutch members 8.1, 8.2 or the disk elements 22.1, 22.2, in particular the disk elements 22.1, 22.2, Can be coupled to each other via This adjusting device 23 is here formed as a piston element 25. The piston element 25 is guided so as to be movable in the axial direction and is preferably guided by the output body 3 in the form of a damper hub 26. The first clutch member 8.1 of the lock-up clutch 8 is advantageously formed by a disk element 22.1 formed by a housing member 45.2. As a result, the element having the friction surface of the lock-up clutch 8 is supported by the housing or supported by the member connected to the input body 2 and is also connected to the output body 3 so as not to be relatively rotatable. In this case, the function of the lock-up clutch 8 is assumed by the housing and the adjusting device 23. The configuration of the lockup clutch 8 is characterized by a small number of components. Output transmission can only take place via frictional surface contact.

  Advantageously, in order to achieve a particularly space-saving construction, the piston element 25 is simultaneously formed as a second clutch member 8.2. In this case, the piston element 25 functions as the disk element 22.2. This disk element 22.2 has a friction surface 24.2. Furthermore, the piston element 25 is here preferably a component of the device 14 for damping vibrations. Accordingly, a series connection is possible between the lock-up clutch 8 and the device 14 for damping vibration with a compact structure. In this case, the piston element 25 simultaneously forms the primary member 15 of the device 14 for damping the vibration. For this purpose, the piston element 25 is formed to have a cylindrical region 27 in the illustrated case. This region 27 is arranged in the region of the outer peripheral surface 28 of the piston element 25 and extends in the axial direction, i.e. parallel to the rotational axis R, and means 17 for torque transmission or means for damping connection. 18. Here, a contact surface 29 against the energy storage unit 19 in the form of a spring unit 20 is formed in the circumferential direction. The contact surfaces 29 are alternately supported by the primary member 15 and the secondary member 16. Here, the secondary member 16 is coupled to the damper hub 26 so as not to be relatively rotatable. Further, the damper hub 26 is coupled to the output body 3 so as not to be relatively rotatable or forms the output body 3. The energy storage unit in the form of a spring unit 20 is here formed, for example, in the form of an arc spring. Other configurations are possible. This configuration of the device 14 for damping vibrations is here characterized in particular by a corresponding housing shape defined by the secondary member 16. For this purpose, the secondary member 16 is adapted to the conditions relating to the configuration space and the shaping in a correspondingly arcuate region in the radially outer region for accommodating the spring unit 19 and in the connection region.

  The structure of the switchable clutch device 10 provided between the turbine wheel T and the device 14 for damping the vibration is similar to that of the first clutch member 10.1 and the second clutch device 10. And a clutch member 10.2. The first clutch member 10.1 is connected to the turbine wheel T so as not to be relatively rotatable. The second clutch member 10.2 cannot be rotated relative to the secondary member 16 of the device 14 for damping vibrations. In particular, the secondary member 16 and the damper hub 26 and thus the output body 3 or the transmission input shaft 43 They are connected via a non-rotatable connection. The switchable clutch device 10 has a multi-plate structure. The switchable clutch device 10 has a plurality of elements having friction surfaces on the first clutch member 10.1. These elements can be operatively coupled to corresponding complementary elements of the second clutch member 10.2. In this case, the friction surface can be formed by the individual disc-like elements themselves or by facing. Furthermore, an adjustment device 13 is disposed corresponding to the clutch device 10. The clutch members 10.1, 10.2 are operatively coupled to each other via the adjusting device 13. The first clutch member 10.1 is coupled to the turbine wheel T so as not to be relatively rotatable. For this purpose, the first clutch member 10.1 has a friction plate support 30 for supporting the first friction plate, here an inner friction plate support, for example, and the second clutch member 10 .2 has a friction plate support 31, in this case an outer friction plate support, which is non-rotatably coupled to the secondary member 16 of the device 14 for damping vibrations. The adjusting device 13 is formed as a piston element 32. The piston element 32 is guided by the damper hub 26 so as to be movable in the axial direction, and extends between the outer friction plate support 31 and the inner friction plate support 30 when viewed in the axial direction. Furthermore, the piston 32 is advantageously guided in a radially movable manner on the outer friction plate support. For this purpose, the piston 32 has a corresponding notch that can engage the guide, similar to the individual friction plates. Both friction plate supports 30, 31 have an L-shaped cross section and are formed in an annular shape. In this case, the friction plate support 30 is preferably connected to the turbine wheel T in a material connection. This similarly applies to the friction plate support 31 with the secondary member 16. Further, the friction plate support 31 can be riveted. Similarly, this also applies to the coupling between the secondary member 16 of the device 14 for damping vibration and the damper hub 26 or the output body 3. This connection is preferably effected by riveting so that it cannot rotate relative to one another.

  The switchable clutch device 10 extends in the radial direction between the damper hub 26 and a partial area outside the device 14 for damping vibrations, in particular the region in which the spring unit 20 is arranged. The extension length in the axial direction is such that, here, the device 14 for damping vibrations has a notch 46 oriented in the axial direction in the form of a pot based on the configuration of the secondary member 16 as a sheet metal forming member. It is formed to form. The switchable clutch device 10 can be accommodated in the notch 46 in the axial direction. Thereby, the arrangement of the switchable clutch device 10 is effected axially within the extended length range of the device 14 for damping the vibrations.

  The force transmission device 1 is formed in a multi-path configuration. For this purpose, the force transmission device 1 is characterized by a plurality of pressure chambers. The first pressure chamber is defined by the working chamber A of the hydrodynamic component 4. The pressure from the work chamber A is also transmitted to the outside of the hydrodynamic type components as seen from the inner chamber 21, that is, the outer peripheral surface in the radial direction from the outlet between the impellers. The pressure in the chamber 21 loads the adjusting device 23 of the lockup clutch 8 and the adjusting device 13 of the switchable clutch device 10. Another chamber that can be loaded with a pressure medium is denoted here by reference numeral 33, and the lock-up clutch is used as an adjusting chamber 23 for loading the piston element 23, here the adjusting device 23 used for the lock-up clutch 8. It functions to not activate 8. Another chamber 34 that can be loaded with a pressure medium is provided for loading the adjusting device 13 of the switchable clutch device 10. This pressure chamber is sealed according to the realization of the functions of the individual elements. In the pressure chamber, at least one connection part 35, 36, 37 for supplying the pressure medium is arranged correspondingly.

  The hydrodynamic rotation speed / torque converter 5 is here formed as a two-pass unit. The connecting portion 35 is arranged corresponding to the work chamber A, and the inner chamber 21 is arranged correspondingly with a working portion 36 for loading the chamber 33 that can be loaded with a pressure medium.

  Another chamber 34 that can be loaded with a pressure medium is arranged corresponding to the switchable clutch device 10. The connection part 37 is connected to the chamber 34. In this case, the connection parts 35 to 37 are guided by corresponding connection elements. In the illustrated example, the pump wheel P is coupled to a so-called “converter hub 38” so as not to be relatively rotatable. The converter hub 38 is rotatably supported. Further, the stator is connected to the stator shaft 39. In this case, the stator can be supported on the stationary element via the one-way clutch F or can be supported on the rotating component of the subsequent output transmission unit depending on the configuration of the converter. Further, here, the connection between the damper hub 26 and the transmission input shaft is shown. In this case, the individual shafts are formed as hollow shafts and are arranged coaxially with each other and are thereby guided in and out. Based on this guidance, a mutually sealable passage can be formed that can be used to guide the pressure medium. This passage is connected to each connection part 35-37. In the simplest case, the connection to the working chamber A via the first connection 35 is performed by means of a driving medium guide or a control medium guide in the driving medium supply system and / or the guiding system 40, the converter hub 38 and the stator shaft 39. Between. The supply to the chamber 34 which can be loaded with a pressure medium is advantageously effected via a connection 37 and an intermediate chamber formed between the transmission input shaft 43 and the stator shaft 39, whereas Supply to the connecting portion 36 for operating the adjusting device 23 of the lockup clutch 8 is performed toward the adjusting device 23 through the transmission input shaft 43. Furthermore, the operating medium supply system and / or the guidance system 40 can be provided with a corresponding valve device for control. This valve device will not be described in detail here. This is because the configuration of the valve device depends on the judgment of those skilled in the art.

  In FIG. 3, the basic structure of the turbine clutch 10 is shown in an exploded schematic view. From this, the friction plate support that can be connected to the turbine wheel T, the friction plate support that can be connected to the secondary member 16, the piston element, and the individual friction plates of the individual clutch members become apparent. These components are fitted inside and outside.

FIG. 4 shows a signal flow chart, in particular by a method according to the invention for controlling a force transmission device during a braking process by a power train 41 used in a vehicle in the form of a hybrid drive, in particular by an electric machine EM operable as a generator. The course for separating the prime mover 11 during the regenerative braking process used in a hybrid drive for converting braking energy into electrical energy and supplying it to the energy storage unit 44 is shown. In this case, the individual clutch devices (locks) when given a signal characterizing the desired braking process, for example a setpoint setpoint value M _brems-soll for a specified braking moment, a delay a _soll or a specified speed v _soll. The state of operation of the up clutch 8 and the switchable clutch device 10) is inspected. First, the lockup clutch 8 is inspected for its operating state. When the lock-up clutch 8 is located in the function state 1, that is, when it is operated, an adjustment signal Y8 is sent to the lock-up clutch adjusting device 23. In the function state 0, which corresponds to the state of being not operated, this causes separation of the output body 3 or the transmission input shaft 43 from the prime mover 11. Similarly, this applies to the second process during the examination of the functional position of the switchable clutch device 10. Again, 1 corresponds to the operating state, and 0 corresponds to the non-operating state. When the switchable clutch device 10 is operated, an adjustment signal Y10 is sent out. In the function state 0, which corresponds to the state of being not operated, this causes separation of the output body 3 or the transmission input shaft 43 from the prime mover 11 via separation of the turbine wheel T. As a result, the prime mover 11 is completely separated from the succeeding transmission, whereby the electric machine EM that can be operated as a generator is controlled, and can be braked regeneratively without loss.

1 is a simple schematic diagram of the basic structure and basic principle of a force transmission device formed according to the present invention provided in a power train with regenerative braking capability; FIG. 1 is an axial sectional view of a particularly advantageous configuration of a force transmission device according to the invention; FIG. It is an exploded view of the structure of a clutch device for turbine wheel separation. 4 is a signal flow chart of the basic course of the method according to the invention for controlling a force transmission device of this type during braking operation in a powertrain with a hybrid drive.

Explanation of symbols

  1 power transmission device, 2 input body, 3 output body, 4 hydrodynamic component, 5 hydrodynamic rotation / torque converter, 6 first output branching unit, 7 direct connection of hydrodynamic component 8 lock-up clutch, 8.1 first clutch member, 8.2 second clutch member, 9 second output branch, 10 switchable clutch device, 10.1 first clutch member 10.2 second clutch member, 11 prime mover, 12 pump wheel shell, 13 adjusting device, 14 device for damping vibration, 15 primary member, 16 secondary member, 17 means for torque transmission, 18 damping Means for connection, 19 Energy storage unit, 20 Spring unit, 21 Interior, 22 .1 disc element, 22.2 disc element, 23 adjusting device, 24.1 friction surface region, 24.2 friction surface region, 25 piston element, 26 damper hub, 27 cylindrical region, 28 outer peripheral surface, 29 contact surface , 30 friction plate support, 31 friction plate support, 32 piston element, 33 chamber, 34 chamber, 35 connection portion, 36 connection portion, 37 connection portion, 38 converter hub, 39 stator shaft, 40 operating medium supply system and / or Or guide system, 41 power train, 42 transmission, 43 transmission input shaft, 44 energy storage unit, 45 housing, 45.1 housing member, 45.2 housing member, 46 notch, 47 device for damping vibration A Work room, EM Electric machine, F one-way clutch, L stator, P pump wheel, R rotation axis, T turbine wheel

Claims (23)

  Multi-functional unit for use in a powertrain (41) with a hybrid drive having at least one electric machine (EM) operable as a generator, in particular as a generator, comprising at least one input A body (2), an output body (3), and a hydrodynamic component (4) disposed between the input body (2) and the output body (3). Device (4) for bypassing the power transmission path via at least one pump wheel (P), turbine wheel (T) and hydrodynamic component (4) 8) and a device (14) for damping vibrations, the force transmission device (1) separates the turbine wheel (T) from the output body (3). Switchable clutch device (10) for the turbine wheel (T) when viewed in the direction of force transmission between the input body (2) and the output body (3). For damping vibrations arranged in parallel to the device (7, 8) for bypassing the output transmission path in series with the hydrodynamic component (4) (14) and the device (7, 8) for detouring the output transmission path via the hydrodynamic component (4) are arranged in series.   2. The force transmission device according to claim 1, wherein the device for damping vibration (14) is arranged in parallel to the clutch device (10).   The device (14) for damping the vibration is transferred from the input body (2) to the output body (3) to the device (7, 8) for bypassing the output transmission path via the hydrodynamic component (4). The force transmission device according to claim 1, wherein the force transmission device is disposed as viewed in the direction of force transmission to.   The elements of the device (7, 8) for bypassing the output transmission path via the hydrodynamic component (4) are components of the device (14) for damping vibrations. 4. The force transmission device according to any one of up to 3.   5. The force transmission device according to claim 1, wherein the element of the clutch device is a component of the device for damping vibration.   The devices (7, 8) for bypassing the output transmission path via the hydrodynamic component (4) have a lock-up clutch (8), and the lock-up clutch (8) It is formed as a connective clutch, which has at least one first clutch member (8.1) and a second clutch member (8.2), both clutch members (8 .1, 8.2) can be operatively coupled to each other via an adjusting device (23).   The force transmission device according to claim 6, wherein the adjusting device (23) and the second clutch member (8.2) are formed by one component.   The joint between the input body (2) and the pump wheel (P) is formed by a housing (45) rotating together, the first clutch member (8.1) being a housing The force transmission device according to claim 6 or 7, wherein the force transmission device is formed by a partial region of (45).   A switchable clutch device (10) for separating the turbine wheel (T) is formed as a frictionally connected clutch, the clutch comprising a first clutch member (10.1) and a second clutch. 9. A member according to claim 1, wherein both clutch members (10.1, 10.2) are operatively coupled to each other via an adjusting device (13). The force transmission device according to claim 1.   Each adjusting device (23, 13) has a piston element (25, 32) that can be loaded with a pressure medium, and the piston element (25, 32) is pressure-liquid tightly connected to the input body (2). The chamber (33, 34) that can be loaded with a pressure medium or a control medium is formed in the output body (3) or the elements of the turbine wheel (T) and the clutch device (10), and is supported so as to be movable in the axial direction. The force transmission device according to any one of claims 6 to 9.   The device for damping vibration (14) comprises a primary member (15) and at least one secondary member (16), both members (15, 16) being arranged coaxially with each other. And are circumferentially restricted and rotatable relative to each other and connected to each other via means for torque transmission (17) and means for damping connection (18). Item 11. The force transmission device according to any one of Items 1 to 10.   The means for torque transmission (17) and / or the means for damping connection (18) comprises a spring unit (20), which spring unit (20) comprises a primary member (15) and a secondary member. The force transmission device according to claim 11, supported by the member (16).   The device for damping vibration (14) is formed as a hydraulic damper, which has a damping chamber that can be filled with a hydraulic liquid as a means for damping connection. The force transmission device according to any one of claims 1 to 12.   The piston element (23) of the device (7, 8) for the primary member (15) of the device (14) for damping the vibration to bypass the output transmission path via the hydrodynamic component (4) The force transmission device according to claim 11, wherein the force transmission device is formed by:   The secondary member (16) is formed as a pot-shaped molded member that forms a notch (46) oriented in the axial direction, and can be switched within the axially extending length of the molded member. 15. A force transmission device according to any one of claims 11 to 14, wherein a simple clutch device (10) is arranged.   A first clutch member (10.1) of a switchable clutch device (10) for separating the turbine wheel (T) is coupled to the turbine wheel (T) so as not to rotate relative to the second wheel. A clutch member (10.2) is coupled to the secondary member (16) of the device (14) for damping vibration so as not to rotate relative to each other, and both clutch members are provided with friction plate supports. It has a plate assembly, the friction plate support is joined to the connecting element in a non-rotatable manner, forming an axial stopper, and the adjusting device (13) has a piston element 17. The piston element according to claim 9, wherein the piston element is guided by one friction plate support in the region of its outer peripheral surface and partitions a pressure chamber (34) that can be loaded with a pressure medium. Power transmission device according to item   The hydrodynamic component (4) is formed as a hydrodynamic speed / torque converter, in particular as a three-element one-stage two-phase converter, and has at least one stator (L), The force transmission device according to any one of claims 1 to 16, wherein the stator (L) is supported by a stationary or rotating element via a one-way clutch (F).   17. The force transmission device according to claim 1, wherein the hydrodynamic component (4) is formed as a hydrodynamic clutch.   The pump wheel (P) is connected to the pump wheel shell (12) in a relatively non-rotatable manner, and the pump wheel shell (12) transmits the force to the turbine wheel (T) in the axial direction and in the radial direction. An intermediate chamber (21) for accommodating another element of the device, the pump wheel shell (12) being a component of the housing (45) of the force transmission device (1), The force transmission device according to any one of claims 1 to 18.   An operating medium supply / guide system (40) is disposed corresponding to the force transmission device (1), and the operating medium supply / guide system (40) is hydrodynamic type via the first connection (35). A chamber (A) that is connected to the working chamber (A) of the component (4) and is temporarily formed in the inner chamber (21) via the second connecting portion (36) and can be loaded with a pressure medium ( 33), which is connected in the region of 33), and is arranged corresponding to the adjusting device (13) of the clutch device (10) that can be loaded with the pressure medium and can be switched via the third connecting portion (37). The force transmission device according to claim 1, wherein the force transmission device is connected to the power transmission device.   21. A power train (41) for use in a vehicle, in particular, is provided with a first prime mover (11), the prime mover (11) being a force transmission device according to any one of claims 1 to 20. An electric machine (EM) that can be connected to the output transmission unit (42) via (1) and can be operated as at least a generator is provided, and the electric machine (EM) can be switched by a clutch device (10 ), A power train characterized by being placed after.   The power train according to claim 21, wherein the electric machine (EM) is arranged coaxially with respect to the power train (41).   The method for controlling the operation mode of the force transmission device according to any one of claims 1 to 20 provided in the power train according to claim 21, wherein the target value, delay and When setting the prescribed braking moment, check the operation of the device (7, 8) for bypassing the output transmission path via the hydrodynamic component and the switchable clutch device (10). In operation, the device (7, 8) for bypassing the output transmission path via the hydrodynamic component and the switchable clutch device (10) are disengaged, A method for controlling the operating mode of a force transmission device provided in a power train, characterized in that a machine (EM) is controlled to generate a braking moment.

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