EP3655276A1 - Module hybride - Google Patents

Module hybride

Info

Publication number
EP3655276A1
EP3655276A1 EP18746083.7A EP18746083A EP3655276A1 EP 3655276 A1 EP3655276 A1 EP 3655276A1 EP 18746083 A EP18746083 A EP 18746083A EP 3655276 A1 EP3655276 A1 EP 3655276A1
Authority
EP
European Patent Office
Prior art keywords
plate
clutch
disk carrier
axially
counter
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP18746083.7A
Other languages
German (de)
English (en)
Inventor
Dirk Reimnitz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP3655276A1 publication Critical patent/EP3655276A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
    • B60K6/38—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the driveline clutches
    • B60K6/387—Actuated clutches, i.e. clutches engaged or disengaged by electric, hydraulic or mechanical actuating means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/48—Parallel type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/60—Clutching elements
    • F16D13/64—Clutch-plates; Clutch-lamellae
    • F16D13/68—Attachments of plates or lamellae to their supports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/70—Pressure members, e.g. pressure plates, for clutch-plates or lamellae; Guiding arrangements for pressure members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/02—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways
    • F16D21/06—Systems comprising a plurality of actuated clutches for interconnecting three or more shafts or other transmission members in different ways at least two driving shafts or two driven shafts being concentric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/06—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch
    • F16D25/062—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces
    • F16D25/063—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially
    • F16D25/0635—Fluid-actuated clutches in which the fluid actuates a piston incorporated in, i.e. rotating with the clutch the clutch having friction surfaces with clutch members exclusively moving axially with flat friction surfaces, e.g. discs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/08—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member
    • F16D25/082—Fluid-actuated clutches with fluid-actuated member not rotating with a clutching member the line of action of the fluid-actuated members co-inciding with the axis of rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D25/00—Fluid-actuated clutches
    • F16D25/10—Clutch systems with a plurality of fluid-actuated clutches
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
    • B60K6/48—Parallel type
    • B60K2006/4825—Electric machine connected or connectable to gearbox input shaft
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2200/00—Type of vehicle
    • B60Y2200/90—Vehicles comprising electric prime movers
    • B60Y2200/92—Hybrid vehicles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/22—Friction clutches with axially-movable clutching members
    • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
    • F16D13/385—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs double clutches, i.e. comprising two friction disc mounted on one driven shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/60—Clutching elements
    • F16D13/64—Clutch-plates; Clutch-lamellae
    • F16D13/69—Arrangements for spreading lamellae in the released state
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D21/00—Systems comprising a plurality of actuated clutches
    • F16D21/08—Serially-arranged clutches interconnecting two shafts only when all the clutches are engaged
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/60—Other road transportation technologies with climate change mitigation effect
    • Y02T10/62—Hybrid vehicles

Definitions

  • the invention relates to a hybrid module for a drive train of a motor vehicle, comprising an electric machine, a coupling device and a separating clutch, wherein the separating clutch is coupled on the one hand with a dual mass flywheel and on the other hand with an intermediate shaft and a frictionally engageable package comprising a pressure plate, a counter plate and at least one Intermediate plate and between these engaging clutch plates, wherein the pressure plate, the intermediate plate and the clutch discs are axially movable.
  • Such a hybrid module installed in a drive train of a motor vehicle is known to drive the vehicle either alone via an internal combustion engine that can be switched on via the hybrid module, via an electric machine, ie an electric motor or both, or if necessary to recuperate energy via the electric machine and so on the vehicle or the vehicle at standstill to charge the battery, for which the electric machine, then driven by the internal combustion engine, runs in generator mode.
  • the hybrid module thus makes it possible to selectively switch the internal combustion engine, ie the internal combustion engine, the electric machine or both torque transmitting in the drive train, including various couplings are provided.
  • the hybrid module itself is coupled on one side with the internal combustion engine, wherein on this side the dual mass flywheel, is provided, ie a flywheel, which is followed by a separating clutch.
  • the disconnect clutch When the disconnect clutch is closed, the torque generated by the internal combustion engine can be transmitted to an intermediate shaft coupled to the disconnect clutch, which is non-rotatably connected to the rotor of the electric machine.
  • the rotor of the electric machine is connected to one or more output shafts leading to the transmission via a clutch device, which may be a dry or wet single or double or multiple clutch.
  • the internal combustion engine can be switched on and regulated via the separating clutch as to whether and which torque is between see the internal combustion engine and the electric machine respectively the rotor is transmitted. This torque can then be transmitted to the one or more output shafts via the rotor and the downstream coupling device.
  • the torque generated by the internal combustion engine can be transmitted in both directions.
  • the internal combustion engine transmits torque to the electric machine during internal combustion engine driving and / or battery charging, while the electric machine transmits torque to the internal combustion engine, for example, to start the internal combustion engine or to utilize the engine braking function.
  • the torque is transmitted as described via the single, double or multiple clutch. If the vehicle is to be driven purely electrically, then the separating clutch is open, the internal combustion engine is not switched on. The electric machine operates, the torque generated on the rotor side is transmitted via the coupling device to the output shafts.
  • both drive means A simultaneous operation of both drive means is conceivable, that is, both the internal combustion engine and the electric machine are switched on the respective couplings, wherein the torque generated by the electric machine side is superimposed on the torque generated on the motor side.
  • such a hybrid module is designed as a so-called P2 hybrid module consisting of a dry disconnect clutch, a wet dual clutch, the corresponding clutch actuation systems, which thus serve to open and close the respective clutch, and the electric machine, wherein the individual components designed and arranged as compact as possible are.
  • the dual clutch is integrated into the rotor, resulting in an axially short module.
  • the separating clutch usually called K0
  • the dual clutch with their individual part clutches commonly called K1 and K2
  • two also individually functioning clutch units which can therefore be operated separately.
  • the clutches are self-opening clutches.
  • All three clutches are therefore realized in a multi-disc or lamellar construction comprising a plurality of individual discs or plates whereby per clutch at least four, usually more friction surfaces arise, which can be compressed by the force of each connected to the clutch actuating system.
  • These actuation systems are mostly housed within the hybrid module housing and consist essentially only of the actuation or support bearings as well as cylinder-piston assemblies actuated by a pressure medium supplied by aggregates outside the hybrid module housing.
  • the pistons are moved in the cylinders and thus exert a force that can be transmitted via the actuating or support bearings on the clutches.
  • All three actuating systems can be controlled independently of each other, so that the three clutches can be operated independently.
  • a pressure medium a hydraulic oil or a brake fluid is usually used, but also a pneumatic operation is conceivable.
  • the couplings of the hybrid module can be operated wet or dry.
  • Wet means that the friction surfaces of the clutches are cooled by a liquid and / or the friction conditions are influenced by a liquid. This requires a corresponding seal of the respective room in which the coupling is provided.
  • the separating clutch dry and the coupling device so for example, the double clutch to perform wet running, and the two rooms via a corresponding partition and a suitable seal from each other to separate.
  • a reverse construction is conceivable. There is always a need to provide an even more compact compared to known hybrid modules hybrid module, which is why the invention is based on the object to provide a similar compact hybrid module.
  • a two-mass flywheel fixed outer disc carrier is provided on which the counter-plate, the intermediate plate and the pressure plate are releasably coupled, wherein the counter-plate rotationally fixed and the intermediate plate and the pressure plate axially are movably connected to the outer disk carrier, and that the clutch discs are arranged axially movable on a réellela- mellenlasi, which is axially fixed in position and rotatably connected to the intermediate shaft.
  • the outer disk carrier is in a fixed connection to the dual mass flywheel, which has for this purpose, for example, a corresponding radial flange to which the outer disk carrier is fastened.
  • the outer disk carrier may, for example, have a radial flange which bears against the radial flange of the dual mass flywheel, so that the fastening can take place in this area.
  • the outer disk carrier has quasi an L-shaped cross-section. The attachment can be done for example by means of separate fastening means, such as screws or preferably rivets, alternatively, welded joints can be used.
  • the outer plate carrier preferably has an axially extending internal toothing, into which the plates engage with respective external toothings.
  • the counter-plate is also fixed in position here, for which purpose it is supported on a corresponding, axially fixed to the intermediate shaft bearing.
  • the counter-plate extends with a suitable flange to the bearing, it has a corresponding bearing seat, in which the bearing is pressed with its outer ring.
  • the pressure plate in turn is coupled to a corresponding actuating system, via which it can be displaced axially, wherein the actuating system is a piston-cylinder unit which operates hydraulically or pneumatically can, and has a corresponding on this piston-cylinder unit axially displaceable support bearing on which the pressure plate is supported.
  • the pressure plate is moved axially, it applies to the adjacent clutch disc, which is taken along and then also runs against the adjacent intermediate plate, which then runs against the next clutch disc, which against the Counter plate is running.
  • the mounting interface is here between the outer disk carrier, which is fastened to the dual mass flywheel, that is to say the engine side, and the other separating coupling parts, in this case the counterplate, the intermediate plate and the pressure plate.
  • the two clutch discs are mounted axially movably on an inner disc carrier.
  • This inner disk carrier in turn sits directly on the intermediate shaft, it is rotatably connected to this.
  • the inner disc carrier is also fixed axially in both directions so that it can not move.
  • the inner disk carrier preferably has a flange, to which a hub adjoins, which is penetrated by the intermediate shaft.
  • the intermediate shaft has an external toothing and the hub has an internal toothing, which engage in one another.
  • the bearing is included
  • a further annular collar which serves as a stop, attached to its inner ring, on the opposite side, for example, a locking ring which is inserted into a Wuwellen workede groove provided as an axial securing means.
  • a locking ring which is inserted into a Wuwellen workede groove provided as an axial securing means.
  • an axial fixing of the inner disk carrier respectively the hub, which is supported on this side, so to speak, on the inner ring of the bearing, and which is supported on the other side on the shaft side annular collar, can be achieved.
  • the electric machine and the coupling device are arranged in a further development of the invention in a first housing space and the separating clutch in a second housing space, of which one, preferably the first housing space, a wet room and the other, preferably the second housing space, a drying room. It is necessary to separate the two housing chambers via a partition wall from one another, and to provide a sealing element which seals the two housing chambers to the intermediate shaft. Due to the fact that due to the axial fixing of the inner disk carrier respectively its hub no axial space for movement to be provided on the intermediate shaft, there is the possibility that corresponding sealing means as close as possible, so adjacent to the inner disk carrier respectively to position the hub. This leads to a further compaction respectively offers the possibility of the intermediate shaft on the support wall, which can be formed axially extended, via two separate bearings, which are axially spaced from each other, to store.
  • the sealing element which is fastened to the intermediate wall, for example, and bears against the intermediate shaft by means of a sealing section, is arranged radially inside a support bearing via which the pressure plate is axially supported.
  • the pressure plate via a corresponding abutment on a support bearing, which is part of the actuating element, supported and rotatably mounted relative to the intermediate wall.
  • This annular bearing is spaced from the intermediate shaft.
  • At least one alignment element is provided, the outer teeth formed on the pressure plate, the intermediate plate and the counter plate, which engage in an axially extending internal toothing of the outer disk carrier, at least during insertion of the external teeth in the internal toothing aligns the outer disk carrier axially.
  • the mounting interface is between the outer plate carrier and the three plates.
  • the alignment element which is designed for example as an annular element and having axially extending fingers or tabs which engage through the plate teeth, so are arranged in the tooth spaces, so that the teeth are aligned. Over this a facilitated joining of the toothings is possible.
  • the Ausrichteiement has a Umgriffabêt at both ends, wherein the one handle section to the counter-plate and the other Umgriffabites surrounds the pressure plate for axial securing.
  • the Ausrichteiement is therefore also an axial securing function over which the assembled parts of the separating clutch are held together axially, so that there is a pre-configurable assembly.
  • the Umgriffabites on one side, which engages around the counter-plate, for example, as a radial flange or flange portion from which the teeth engaging in the fingers extend axially, which rests flat against the counter-plate. In this area can also be a permanent attachment to the counter plate.
  • the Ausrichteiement example be slightly bent or flared, so that the pressure plate is engaged behind the local.
  • the aligning element with its or its sections passing through the outer teeth, is so narrow that it engages with play between the respective outer toothing.
  • the Ausrichteiement is not loaded in the torque-transmitting operation, that is, it does not participate in the power flow, so has no function and therefore can remain in the installed state in position.
  • each one or more spring elements are provided between the pressure plate and the intermediate plate and between the intermediate plate and the counter plate.
  • These spring elements serve to reopen the disconnect clutch after relieving it from the actuation system, ie to ventilate it and to push the corresponding coupled plates apart so that the frictional connection is released.
  • the spring elements are preferably coil springs, which are inserted into the formed on the outer disk carrier internal teeth. It can have separate spring elements be provided, or connected to corresponding ring packages spring elements.
  • FIG. 1 is a schematic diagram of a hybrid module of a first embodiment
  • FIG. 2 is a schematic representation of a hybrid module of a second embodiment
  • FIG. 3 is a schematic diagram of a hybrid module of a third embodiment
  • FIG. 4 shows a schematic representation of a hybrid module of a fourth embodiment
  • FIG. 5 shows a schematic illustration of a hybrid module of a fifth embodiment
  • FIG. 4 shows a schematic representation of a hybrid module of a fourth embodiment
  • FIG. 5 shows a schematic illustration of a hybrid module of a fifth embodiment
  • FIG. 4 shows a schematic representation of a hybrid module of a fourth embodiment
  • FIG. 5 shows a schematic illustration of a hybrid module of a fifth embodiment
  • Figure 6 is a schematic diagram of a hybrid module of a sixth embodiment.
  • FIG. 1 shows a hybrid module 1, comprising a case only indicated here 2, in which a wet room 3 is provided, which is separated by a partition wall 4 of a drying room 5, wherein the intermediate wall 4 to the housing 3 of course closed respectively sealed.
  • a drying room 3 there is an electric machine 6 with a stator 7 and a rotor 8 and a coupling device 9 comprising a first part clutch 10, usually called K1, and a second part clutch 1 1, usually called K2.
  • the two partial clutches 10, 1 1 have a common outer plate carrier 12, which is fixed to the Ro tor 8 is connected.
  • first and second disks 13, 14 are axially movably guided via a corresponding toothing engagement, for which purpose the outer disk carrier 12 has an internal toothing and the disks 13, 14 have an outer toothing.
  • the fins 13, 14, which may also be referred to as outer fins engage further fins 15, 16, which may also be referred to as inner fins, a.
  • the first inner disks 15 are guided axially movably on an inner disk carrier 17, which has an outer toothing in which the inner disks 15 engage with an internal toothing.
  • the second inner disks 16 engage with a corresponding internal toothing in the outer toothing of a second inner disk carrier 18 and are also guided axially movable there.
  • the first inner disk carrier 17 is connected via a hub 19 with a first, leading to the transmission output shaft 20, the second inner disk carrier 18 is connected via a hub 21 with a second, also leading to the transmission output shaft 22.
  • each actuation system 23, 24 each having a pressure pot 25, 26 which is rotatably mounted via a corresponding bearing 27, 28 relative to a positionally fixed piston-cylinder arrangement 29, 30.
  • the respective pressure pot 25, 26 are moved axially. He presses the corresponding disk set consisting of the outer and inner disks 13, 15 and 14, 16 against a respective abutment 31, 32, about which the respective disk set is closed.
  • a frictional engagement is formed within the individual part couplings 10, 11, so that a torque resting on the outer disk carrier 12 can be transmitted to the respective inner disk carrier 17, 18 and from there to the respective output shaft 20, 22.
  • the outer disk carrier 12 is fixedly connected to an intermediate shaft 33 which, via a bearing 34, is non-rotatable with respect to the intermediate wall 4 or the general housing arrangement is stored.
  • the intermediate wall 4 is sealed by a corresponding sealing element 34 to the intermediate shaft 33 out.
  • a disconnect clutch 35 is coupled to the intermediate shaft 33 to a dual mass flywheel 36, which in turn is connected to a crankshaft flange 37.
  • the coupling shaft flange 37 in turn is connected to the internal combustion engine, so it is driven by this.
  • the disconnect clutch 35 which can also be referred to as a knock-out clutch, serves to couple the internal combustion engine if required in order to transmit a torque delivered via the internal combustion engine via the intermediate shaft 33 to the rotor 8 and thus to the outer disk carrier 12, so that the torque optionally via the first or second partial clutch 10, 1 1 to the respective coupled output shaft 20, 22 can be transmitted.
  • the separating clutch 35 has an outer disk carrier 38, which has an axially extending internal toothing. This internal toothing simultaneously forms an external toothing, which also extends axially, from. By the dashed portion 39, the combined inner external toothing is shown.
  • the separating clutch 35 comprises a counter-plate 40, which is axially fixed in position and which is fixedly connected to the outer disk carrier 38, which has a corresponding radial flange 73 in this area. This can be done for example by riveting or welding.
  • an intermediate plate 41 and a pressure plate 42 which engage in the internal toothing of the outer plate carrier 38 via corresponding external teeth and are guided in a rotationally fixed manner, but axially movable.
  • a clutch disc 43, 44 both of which are non-rotatably connected via a corresponding hub 45 with the intermediate shaft 33.
  • the clutch disc 43 is connected via a curved connecting flange 46 with the hub 45, the clutch disc 44 is connected via a drive plate 47 with the connecting flange 46.
  • the hub 45 is, since the clutch plates 43, 44 must be axially movable, on the intermediate shaft 33, which is externally toothed and with which the hub 45 is rotatably connected via a corresponding internal toothing, guided axially movable.
  • the pressure plate 42 is rotatably supported by a bearing 48 relative to the intermediate wall 4.
  • the bearing 48 is in turn part of an actuation system 49, which also includes a piston-cylinder unit 50, which can be hydraulically or pneumatically operated as well as the other piston-cylinder units already described.
  • the bearing 48 can be moved axially and with him the pressure plate 42 so that it is axially displaced while the clutch plates 43, 44 and the intermediate plate 41 axially entrains and so brings this disk set in frictional engagement.
  • This displacement movement takes place against the restoring force of a plurality of spring elements 51, which are arranged between the counter-plate 40 and the intermediate plate 41 respectively of the intermediate plate 41 and the pressure plate 42 in the region of the internal teeth of the outer disk carrier 38.
  • Several separate individual spring elements 51 can be positioned distributed around the respective circumference, but also corresponding spring packages coupled to form a ring.
  • the latter For coupling the dual-mass flywheel 36, the latter has a radial flange 52, which has an internal toothing 53 which meshes with the external toothing of the outer disk carrier 38, ie engages in this.
  • a torque transmitted from the internal combustion engine via the coupling shaft flange 37 to the dual mass flywheel 36 can be transmitted from the dual mass flywheel 36 to the outer disk carrier 38 and via the separating clutch 35 itself to the intermediate shaft 33 and from this via the dual clutch to the corresponding output shaft 20. 22.
  • the central assembly is the disconnect clutch 35 and its coupling to the dual mass flywheel.
  • the clutch plates 43, 44 can be clamped in each case for torque transmission frictionally between their neighboring components, so the respective plates 40, 41, 42 upon actuation of the actuating system 49.
  • the two clutch plates 43, 44 are axially displaceable, but rotatably connected to the intermediate shaft 33.
  • the axially fixed counter-plate 40, the axially limited displaceable intermediate plate 41 and the axially limited displaceable pressure plate 42 are rotatably connected to the dual-mass flywheel 36.
  • the actuation system 49 connected to the clutch 35 pushes the pressure plate 42 against the first clutch disc 44.
  • the first clutch plate 44 then applies to the intermediate plate 41 so that then the pressure plate 42, the clutch disc 44 and the intermediate plate 41 axially displaced be until the intermediate plate 41 meets the further clutch disc 43 and presses against the axially fixed counter-plate 40.
  • the counter-bearing plate 40 is supported via a bearing 54 on the intermediate shaft 33.
  • This bearing 54 initiates the axial actuating forces in the intermediate shaft 33, but also ensures the centering, support and positioning of the separating clutch 35.
  • this bearing 54 is designed as angular contact ball bearings or deep groove ball bearings.
  • the bearing 54 is pressed into a formed on the counter-plate 40 bearing seat 55, which ensures a radial and axial positive locking.
  • this is done by a shaft securing ring 56 which is inserted into a corresponding groove on the intermediate shaft 33.
  • further components between the counter-bearing plate 40 and the bearing 54 and / or between the bearing 54 and the intermediate shaft 33.
  • the bearing diameter significantly larger than the diameter of the intermediate shaft 33.
  • the counter-plate 40, the intermediate plate 41 (of course, several may be provided, which then has the consequence that also a plurality of clutch discs are provided) and the pressure plate 42 are connected by the outer disc carrier 38 with each other. This is as described firmly connected to the counter-plate 40, for example, by welding or riveting.
  • the intermediate plate 41 and the pressure plate 42 are axially movable relative to the outer disk carrier 38, but held by this form-fitting radially and in the circumferential direction.
  • the outer disc carrier 38 thus ensures that the intermediate plate 41 and the pressure plate 42 remain within their desired range of motion.
  • the outer disk carrier ensures the torque transmission between the pressure plate 42, the intermediate plate 41, the back plate 40 and the dual mass flywheel 36.
  • the described combined internal-external toothing As described, it is expediently with a running in the axial direction and in the circumferential direction repeated tooth contour, the described combined internal-external toothing , fitted.
  • the spring elements 51 here helical compression springs, are provided between the counterplate 40 and the intermediate plate 41 and the intermediate plate 41 and the pressure plate 42. These spring elements 51 push the intermediate plate 41 and the pressure plate 42 back into its open position when the pressure of the pressure medium in the piston-cylinder unit 50 has dropped far enough. The spring elements 51 also push the piston of the piston-cylinder unit 50 back into its starting position.
  • the separating clutch 35 may be equipped with circumferential spring elements 51 or with a plurality of spring elements 51 arranged around the circumference, wherein the spring elements 51 are held in position by the participating plates and / or the plate carrier 38.
  • the mounting interface between these two units is placed, specifically between the two-mass flywheel 36 and the clutch 35.
  • the dual-mass flywheel 36 is bolted to the crankshaft flange 37 and thus is part of the engine for the assembly process.
  • the separating clutch 35 is mounted on the intermediate shaft 33, which is mounted on the support wall 4 connected to the housing 2.
  • the disconnect clutch 35 for the assembly process is part of the transmission.
  • the radial flange 52 is provided in the embodiment shown with an internal toothing, which engages in the toothed outer contour, ie the outer toothing of the plate carrier 38, wherein, as Figure 1 shows, the partial clutch 35 is at least partially inserted into the dual-mass flywheel 36 for this purpose.
  • the plug or toothed connection can be biased in the circumferential direction. Such biasing capability will be described below with reference to FIG.
  • a clamping component which can be rotated relative to the disk carrier 38 can be used for this purpose, which engages radially outward in the region of the plug-in or toothed connection and which is braced in the circumferential direction by tangentially acting springs.
  • the toothing 53 of the radial flange 52 can thus between the tooth flanks of the external toothing of the outer disk carrier 38, in which create the teeth of the toothing 53 in the one circumferential direction and the fingers or extensions of the clamping member, which engage in this area, and the flange 53 against the Press just mentioned flanks of the outer disk carrier 38, be trapped.
  • the toothing 53 of the radial flange 52 is pushed during assembly of internal combustion engine and transmission between or in the mating contours of outer disk carrier 38 and clamping member.
  • the two clutch plates 43, 44 of the separating clutch 35 are relative to each other, so relative to the intermediate shaft 33, axially limited displaceable, as described. But they are not rotatable among each other as well as relative to the intermediate shaft 33.
  • the clutch disc 43 is fastened to the externally toothed intermediate shaft 33 by means of a hub 45 which is internally toothed.
  • the further clutch plate 44 is connected by an internal toothing or with inwardly projecting extensions with a tooth contour or web-like connecting contours with the clutch disc 43 and the connecting flange 46, respectively.
  • the structure of the separating clutch is basically comparable to the structure, as described in Figure 1. However, different here is the attachment of the outer plate carrier 38, as well as the possibility of integrating an alignment element is shown.
  • the disk carrier 38 which here also has an inner toothing or combined inner-outer toothing indicated by the dashed section 39, is fixedly connected to a radial flange 52 of the dual-mass flywheel.
  • the outer disk carrier 38 connects the disks of the separating clutch 35, that is to say the counter plate 40, the intermediate plate 41 and the pressure plate 42, to one another in a rotationally fixed manner, which also engage in the internal toothing of the outer disk carrier 38 via corresponding external toothings.
  • the counter plate 40 with an external toothing in the internal toothing of the outer disk carrier 38 after it is firmly or respectively inextricably coupled to the dual mass flywheel 36. This means that the entire lamellar arrangement is detachable from the outer disk carrier 38, and therefore the mounting interface between the outer disk carrier 38 and the disk pack is given here.
  • a radially outwardly extending flange 57 is provided on the side of the toothed ring body of the outer disk carrier 38 facing the dual mass flywheel 36.
  • This flange 57 is riveted or welded to the radial flange 52.
  • the connection between the flange 57 and the radial flange 52 is wholly or partially disposed between the sprung friction elements of the dual mass flywheel 36.
  • the outer flange diameter of the flange 57 of the outer disk carrier 38 is thus greater than the inner diameter of the friction element.
  • the inner diameter of the friction element is greater than the outer diameter of the toothed annular body of the disk carrier 38.
  • the bow spring, the friction element to its friction partner, z. B. the cover of the dual mass flywheel, presses, it can be on the outer disk carrier 38 or on the connecting means such as a rivet, via which the outer disk carrier 38 is attached to the radial flange 52, supported.
  • the outer disk carrier 38 Since the outer disk carrier 38 is fixedly connected to the dual mass flywheel 36, the mounting interface between the engine and the transmission between the outer disk carrier 38, which is part of the internal combustion engine, and the remaining separating coupling parts, ie essentially the counter-plate 40, the intermediate plate 41 and the Pressure plate 42, which are part of the transmission.
  • an alignment member 60 is provided in the example shown, which holds the tooth contours of the three toothed plates 40, 41, 42 of the separating clutch 35 in the correct circumferential position.
  • the alignment member 60 not only ensures that the plates 40, 41, 42 can not rotate against each other, but also ensures that the components of the separating clutch 35, including the clutch plates 43, 44 and their Anbin- training components to the intermediate shaft 33rd , already without outer disk carrier 38 a stable sub-assembly, so form a stable assembly.
  • the alignment member 60 thus also serves as a transport lock or captive for the disconnect clutch 35.
  • the alignment member 60 is provided as an annular member secured to the backing plate 40 with a radial flange 61 and having axially extending elongated finger-like extensions 62 extending through the tooth gaps of the separation clutch plates 40, 41 , 42 pass through to the back of the pressure plate 42.
  • the extensions 62 are bent, so have a radially inwardly bent edge 63, which engages behind the pressure plate 42. This bending takes place when all components including the pressure plate 42 have been inserted into the alignment element 60. This grip ensures that the components can not fall out.
  • the alignment element 60 thus represents a type of replacement disk carrier, which takes over all tasks of the not yet present outer disk carrier 38 from the clutch assembly, so if the clutch is mounted as a subassembly, until the assembly of the internal combustion engine with the transmission. Since the projections 60 of the alignment element near the root circle run in the tooth gaps of the toothings of the plates 40, 41, 42, the alignment element 60 covers the main part of the Tooth flanks of the plates 40, 41, 42 not off. When the outer disk carrier 38 is inserted into the tooth spaces of the plates 40, 41, 42, the tooth flanks of the plates 40, 41, 42 can thus bear directly against the tooth flanks of the internal toothing of the outer disk carrier 38.
  • the plates 40, 41, 42 in the alignment element 60 have slightly more clearance in the circumferential direction than in the outer toothing of the disc carrier 38. This ensures that the torque transmission from the plates 40, 41, 42 directly on the outer disk carrier 38 takes place without the alignment element 60 having to transmit peripheral forces during operation of the separating clutch 35.
  • the alignment element 60 thus has, with regard to the orientation and guidance of the plates, no longer any function during the operation of the separating clutch 35. Therefore, it also does not hinder the axial displacement of the plates 40, 41, 42 or the clutch plates 43, 44. If possible, the spring elements 51 installed in the disconnect clutch 35 are positioned over the alignment element 60, then the alignment element 60 can perform this function fulfill the entire coupling service life.
  • the alignment element 60 is preferably designed as a sheet metal part, ie as a simple stamping and deep-drawing component.
  • a plurality of separate alignment elements arranged around the circumference can also be used.
  • the alignment member 60 may on the internal combustion engine side facing the counter plate 40 also have one or more contour elements or Ein Industrieskonturen, the insertion of the outer teeth of the outer disk carrier 38 in the tooth gaps of the counter-bearing plate 40, and thus also the axially aligned teeth of the intermediate plate 41 and the Pressure plate 42 made easier.
  • These insertion contours can be in particular in the radial and / or tangential direction beveled surfaces which are arranged around the tooth spaces of the counterplate toothing.
  • connection carrier provided with an internal toothing would be fixedly attached to the radial flange 52 of the dual mass flywheel 36, similar to the outer disk carrier 38 according to FIG. 3.
  • the outer disk carrier 38 would then be part of the separating clutch 35, similar to FIG described, and firmly connected to the counter-bearing plate 40.
  • the dual mass flywheel connecting carrier (similar to in Figure 2) axially into the outer toothing of the outer disk carrier 38, which is similar to Figure 1 fixed to the counter-plate 40 of the clutch 35, insert.
  • the connection carrier fixedly connected to the dual mass flywheel 36 then transmits the torque of the motor to the outer plate carrier 38 fixedly connected to the counterplate 40, which then transmits the torque to the plates 40, 41, 42 of the separating clutch 35.
  • the connecting carrier has, as well as the outer disk carrier 38, an approximately circular area, which has radially inwardly and radially outwardly an axially extending and repeating in the circumferential direction tooth contour.
  • the connection carrier may be preferably designed as a sheet metal part, the material thickness in the region of the toothing is small in relation to the size of the teeth, as well as the outer disk carrier 38. This follows the material in the circumferential direction of a meander shape to the combined inner and To be able to train external teeth.
  • the outer toothing of the outer disk carrier 38 forms the mounting interface and torque transmission interface to the radial flange 52 of the dual mass flywheel 36, wherein the radial flange 52 also engages via an internal toothing 53 in the outer toothing of the outer disk carrier 38.
  • the embodiment of the separating clutch 35 shown in FIG. 3 is characterized in that, in addition to the outer disk carrier 38 fixedly connected to the counterplate 40 relative to which the pressure plate 42 and the intermediate plate 41 are axially movable, the pressure plate 42 and / or the intermediate plate 41 are rotatably connected via at least one leaf spring with the outer disk carrier 38 or the counter-plate 40. In the example shown in FIG.
  • both the intermediate plate 41 and the pressure plate 42 are connected to the outer disk carrier 38 via corresponding leaf springs 64 (relating to the intermediate plate 41) and 65 (relating to the pressure plate 42).
  • the outer disk carrier 38 on its side facing the transmission on a circumferential, radially outwardly extending radial flange 66.
  • the outer disk carrier 38 may also have on its side facing the transmission a plurality of circumferentially distributed, extending radially outwardly extending tabs. This radial flange 66 or the tabs are used to attach the leaf springs 64, 65, which support the intermediate plate 41 and the pressure plate 42.
  • both the intermediate plate 41 and the pressure plate 42 is held at three points distributed over the circumference on the leaf springs 64, 65.
  • the leaf springs center the respective plates 41, 42, provide the torque transmission and allow the axial displacement of the plates.
  • the intermediate plate 41 and the pressure plate 42 are also a plurality of circumferentially distributed extensions 67 (to the intermediate plate 41) and 68 (at the Press plate 42) provided on which the leaf springs 64, 65 are attached. So that these extensions 67 do not collide with the plate carrier 38, it has axially extending recesses, ie it is locally longitudinally slotted, so that the extensions of at least the intermediate plate 41, and if appropriate also the extensions of the pressure plate 42, can be inserted into these recesses or slots. when the disc pack is compressed axially.
  • the side of the outer disk carrier 38, to which the leaf springs 64, 65 are attached, thus has the same task as a clutch cover in most commercial couplings.
  • the plate carrier shown in Figure 3 can thus also be replaced by a carrier ring fulfilling the plate carrier function and a clutch cover.
  • the drive ring serves as a connection interface to the dual mass flywheel and the clutch cover supports the leaf springs, which hold the plates of the separating clutch.
  • the counter-plate 40 has radially outer projections, on which the leaf springs are fastened.
  • the counter-plate 40 can be equipped with a collar extending radially beyond the clutch disc 43 arranged next to it in the direction of the transmission, to which a circumferential radial flange or a plurality of radially extending tabs for the leaf spring attachment adjoin in the radial direction.
  • the intermediate plate 41 and pressure plate 42 fastened via the leaf springs 64, 65 can be displaced with less friction than is the case with plates 41, 42 mounted in a plate carrier gearing. Because due to the torque transmitting, fixed connection of the plates 41, 42 with the outer disk carrier 38 via the leaf springs 64, 65 no friction generating gear engagement is given, that is, the elements can be moved without contact axially with respect to each other. As a result, the separating clutch 35 can be controlled and controlled particularly well with plates 41, 42 fastened to the leaf springs 64, 65. In addition, there is no danger that high circumferential accelerations or unfavorable resonance effects lead to rattling noises, as may occur in the case of multi-disc toothings. As an alternative to the example shown in FIG.
  • the counter-plate 40 is fixedly connected to the outer disk carrier 38, while the intermediate plate 41 and the pressure plate 42 on the outer disk carrier 38 rotatably via a toothing engagement, however, are guided axially movable.
  • the outer disk carrier 38 is coupled via a toothed engagement with the dual mass flywheel 36, for which purpose it has a radial flange 52 with an internal toothing 53, which engages in the external toothing of the outer disk carrier 38 in a torque-transmitting manner.
  • one or more the toothing engagement between the outer disk carrier 38 and the dual mass flywheel 36 in the circumferential direction biasing spring elements 69 are provided.
  • These spring elements 69 serve to slightly displace the twin-mass flywheel 36 in the circumferential direction relative to the outer disk carrier 38, so that it is ensured that the flank of the inner toothing 53 always abuts against the adjacent flanks of the outer toothing of the outer disk carrier 38 in a circumferential direction. This serves to avoid unwanted rattling noise within the plug or toothed connection between the dual mass flywheel 36 and the disconnect clutch 35.
  • FIG. 1 In the exemplary embodiment shown in FIG.
  • a tensioning element 70 shown only in dashed lines, which has a radially inwardly extending radial flange 71, from which a plurality of axially extending tabs 72 protrude between the interlocking toothings of the radial flange 52 and the outer disc carrier 38 engage.
  • the clamping element 70 is preferably designed as a ring component, so that only one element is to be mounted.
  • Corresponding recesses or the like are provided on the radial flange 71 so that support sections which form on the radial flange form, on each of which a spring element 69, also here preferably a helical compression spring, is supported.
  • the other end of the respective spring element 69 is supported on the radial flange 73 of the outer disk carrier 38, via which it is connected to the counter-plate 40.
  • the or the spring elements 69 act quasi tangentially, ie in the circumferential direction and thus rotate the outer disk carrier 38 relative to the radial flange 52.
  • the teeth of the toothing 53 can thus between the tooth flanks of the outer toothing of the outer disk carrier 38, in which the toothing 53 in the one circumferential direction applies , and the tabs 72 of the clamping element 70, the gearing 53 press against the mentioned flanks of the external teeth of the Jardinlamellenträ- gers 38, are clamped.
  • a constant contact between two tooth flanks is given, so that rattling can be excluded.
  • the teeth of the toothing 53 of the radial flange 52 are pushed between the counter contours of the external toothing of the outer disk carrier 38 and the lugs 72 of the clamping element 70 during assembly of the internal combustion engine and the transmission.
  • the mounting interface for the assembly of the engine and transmission is also between a fixedly connected to the dual mass flywheel 36 outer disk carrier 38, the shape of which, as described with reference to Figure 2, and optionally on the dual mass flywheel 36th
  • the counter-plate 40, the intermediate plate 41 and the pressure plate 42 does not engage in the internal toothing, again shown on the dashed section suggesting it 39, the outer disk carrier 38, but in this embodiment, the two clutch disks 43, 44 with their corresponding external teeth in the internal toothing of the outer disk carrier 38 axially movable, but guided to transmit torque.
  • the counter-plate 40, the intermediate plate 41 and the pressure plate 42 are rotatably connected to the intermediate shaft 33 here.
  • the counter-plate 40 has a radially extending to the intermediate shaft 33 toward flange 74, to which an internally toothed, by the externally toothed intermediate shaft 33 engages through hub 75 connects.
  • An inner disk carrier 76 is fastened to the counter plate 40 or the flange 74, for example with a radial flange with an L-shaped cross section, riveted or welded thereto, which has an external toothing.
  • This embodiment is thus characterized by the fact that the outer disk carrier 38 is fixedly connected to the dual mass flywheel 36, wherein the outer disk carrier 38, the clutch plates 43, 44 are guided axially movable. Further, a nenlamellennum 76 is provided relative to the pressure plate 42 and the intermediate plate 41 are axially movable and which is fixedly connected to the counter-plate 40, which in turn is fixedly connected to the intermediate shaft 33 rotatably.
  • the counterplate 40 can be fixedly connected to the intermediate shaft 33 as described.
  • a bearing 54 as provided in the above embodiments, is no longer necessary here, since not only the actuating forces are introduced into the intermediate shaft 33 via the counter plate 40, but also the torque transmitted by the separating clutch. Since this clutch assembly does not support its actuating forces on the crankshaft and still requires no bearing 54 for support, this structure offers a large installation space and cost advantage.
  • the separating clutch 35 with the counterpart plate 40 belonging to the internally toothed hub 75 is pushed onto the externally toothed intermediate shaft 33 and secured by a locking ring 77 against unintentional axial displacement.
  • the counter plate 40, the intermediate plate 41 and the pressure plate 42 are as described by the nenlamellennum 76 connected to each other, which is fixedly connected to the counter plate 40, for example by welding or riveting and engages in an internal toothing on the inner diameter of the intermediate plate 41 and the Intermediate plate 41 thereby positioned axially leads and rotatably coupled to the back plate 40.
  • the pressure plate 42 At the opposite end of the counter plate 40 of the inner disk carrier 76 of the latter is connected to the pressure plate 42, which he positioned as well as the intermediate plate 41, axially guides and rotationally coupled to the counter-plate 40.
  • the pressure plate 42 consists of a radially outer part or section, the actual pressing part, and a radially inner flange portion 78, wherein the two parts are radially interconnected by some distributed around the circumference webs. There are thus formed on the pressure plate 42 more openings, which are limited in the circumferential direction over the webs.
  • the radially outer part of the pressure plate 42 forms the friction surface for the adjacent clutch disk 44 and is similar to the intermediate plate 41.
  • the radially outer part of the pressure plate 40 has a tooth contour on its inner diameter in order to be able to engage in the inner disk carrier 76. This tooth contour is interrupted on the circumference several times by the described, radially inwardly extending webs or openings.
  • the radially inner part of the pressure plate 42 is formed as a pressure piece which connects the pressing plate 42 with the support bearing 48 of the actuating system 49.
  • the radially inner part of the pressure plate 42 is, in order to ensure a sufficiently high rigidity, designed as a circumferentially closed area, which, if at all, is penetrated only by small, only slightly affecting the stiffness vents.
  • the webs that connect the radially outer portion and the radially inner portion of the pressure plate 42 together and limit the openings do not abut against the inner disk carrier 76, the inner disk carrier at the points where the ridges are located, recessed.
  • the webs are inserted into the slots between the fingers.
  • the lands may reciprocate axially within these slots as the pressure plate 42 is axially moved by the actuating system 49.
  • the slots of the inner disk carrier 76 reach axially only as deeply into the inner disk carrier 76, as required by the movement region of the pressure plate 42.
  • the remainder of the inner disk carrier 76 is circumferentially closed to provide sufficient rigidity. If it requires ventilation and the rigidity of the inner disk carrier 76 permits it, there may also be isolated small ventilation openings in this area.
  • the distributed on the circumference webs between the radially outer and the radially inner part of the Anpressteil 42 are axially guided in the slots of the mecaniclamellen- carrier 76.
  • the width of the fingers of the inner disk carrier 76 and the width of the apertures is matched to one another such that the pressure plate 42 can be axially guided on the inner disk carrier 76 and rotatably connected thereto.
  • the opening can be assisted by spring elements 51 between the counterplate 40 and the intermediate plate 41 and the intermediate plate 41 and the pressure plate 42.
  • spring elements between the counter-plate 40 and the pressure plate 42.
  • the principle shown in Figure 3 the intermediate plate 41 and / or the pressure plate 42 with leaf springs axially displaceable and torque-transmitting to attach, mutatis mutandis transferred to the separating clutch 35 shown in Figure 5.
  • the leaf springs are then not radially outside the Clutch discs 43, 44, but radially disposed within the clutch disc inner diameter.
  • the two clutch plates 43, 44 can be secured against rotation relative to one another by an alignment element, similar to that described with respect to FIG.
  • an alignment element similar to that described with respect to FIG.
  • the tooth gaps of the two clutch plates 43, 44 are aligned, so that the toothing of the disk carrier 38 fastened to the radial flange 52 of the dual mass flywheel 36 can easily be inserted into the tooth spaces of the clutch disks 43, 44.
  • the details described for the alignment element 60 of the exemplary embodiment according to FIG. 2 can also be analogously transmitted to the alignment element which aligns the two clutch plates 43, 44.
  • the straps serving to align the two disks can also be formed on the already existing clutch disk components, such as the pad spring suspension members.
  • the optionally provided alignment element only has to align the clutch disk toothings. It is not necessary to combine the disconnect coupling components to form a captive subassembly for transport and assembly.
  • This mounting fuse can be realized in the disconnect clutch shown in Figure 5 on the inner disk carrier 36, which holds the disconnect clutch components together by preventing the pressure plate 42 unintentionally slips off the inner disk carrier 76.
  • the edge of the inner disk carrier 76 behind the pressure plate 42 this then hintercitedd be bent (similar to that shown in principle in Figure 1), or it is behind the pressure plate 42, a locking ring 79, as shown in Figure 5, provided which is inserted into a corresponding annular groove on the inner disk carrier 76.
  • These oblique surfaces may be provided on the end of the outer disk carrier 38 remote from the dual mass flywheel 36 and / or on the sides of the clutch disks 43, 44 facing the dual mass flywheel. Nevertheless, it is expedient to design the radially outer portion of the clutch plates 43, 44 robust, so that these areas can endure axial forces that go well beyond the axial forces expected in the later coupling operation.
  • the middle region of the clutch disks 43, 44 which radially outwardly forms the connecting contour to the outer disk carrier 38, already makes up over 25% of the total distance between the two disk friction surfaces present on the two opposite sides of the clutch disks 43, 44 ,
  • the central portion of the clutch plates 43, 44 makes up a significantly greater proportion of the unclamped overall width of the clutch plates 43, 44 than, for example, the pad spring segments and the carrier plates make up with commercially available clutch plates.
  • the separating clutch 35 shown here makes sense to make the axially narrowest circumferentially running region of the respective clutch disc 43, 44, which is located radially between the outer diameter of the friction surfaces and the inner diameter of the connecting contour (tooth contour), axially so wide in that it accounts for 20% -100% of the total distance between the two disc friction surfaces present on the two opposite sides of the unstressed clutch disc 43, 44.
  • the radially slightly spaced from the friction surfaces area of the connection contour (tooth contour) can be made even slightly wider.
  • FIG. 6 shows a further exemplary embodiment of a hybrid module, the basic structure of the separating clutch being similar to that of FIG.
  • the outer disk carrier 38 is again firmly connected via rivet or welded connections to a radial flange 52 of the dual mass flywheel 36.
  • the mounting interface is in turn between the outer disk carrier 38 and releasably coupled with him, rotatably via respective teeth interventions, but axially displaceable components of the clutch 35, here so the counter-plate 40, the intermediate plate 41 and the pressure plate 42 given.
  • the counter-plate 40 is also in turn here via an extended flange portion on which a bearing seat 55 is formed, and rotatably mounted on a bearing 54 on the intermediate shaft 33.
  • the pressure plate 42 in turn is in turn connected via an extended flange portion with the bearing 48 and supported on this, which in turn is axially actuated as part of the actuation system 49 via the piston-cylinder unit 50.
  • the connection of the two clutch plates 43, 44 to the intermediate shaft 33 are according to Figure 6, the two clutch plates 43, 44 connected via a common inner disk carrier 80 with the intermediate shaft 33.
  • the inner disk carrier 80 has an external toothing 81 into which the coupling letters 43, 44 engage with corresponding internal toothings 82, 83.
  • the clutch plates 43, 44 are consequently guided axially movably on the inner disk carrier 80, but are non-rotatable and thus momentary. transferring connected to the inner disk carrier 80.
  • the inner disk carrier 80 can thus be rigid, so axially fixed position and rotatably connected to the intermediate shaft 33, so it is itself, unlike the above embodiments according to Figures 1 - 4, axially non-movable, since the axial movement in the region of the meshing engagement on the inner disk carrier 80th takes place to the clutch plates 43, 44.
  • Such a connection of inner disk carrier 80 to the intermediate shaft 33, in which no sliding movements occur, can be made significantly smaller than, for example, in the example shown in Figure 2.
  • the axial space thus obtained was used in the hybrid module 1 shown in FIG. 6 to move the sealing element 34, which separates the wet space 3 from the drying space 5, axially in the direction of the
  • FIG. 6 shows, for example, a bearing with two separate bearings 84, 85, instead of the one double-row bearing 86, as shown in the preceding exemplary embodiments.
  • the inner disk carrier 80 has for connection to the intermediate shaft 33 has a radially inwardly extending flange 87 and an adjoining, internally toothed hub 88 which engages in an external toothing on the intermediate shaft 33. Axially in one direction, the inner disk carrier 80 is supported on an annular collar-like stop 89 of the intermediate shaft 33, on the other side, the Abstützung via the axially fixed bearing 54 and its inner ring.
  • the sealing element 34 connects, which in the embodiment shown within the support bearing 48, over which the pressure plate 42 is axially supported, is positioned.
  • an alignment element 60 is likewise provided, which axially aligns the external plate teeth formed on the pressure plate 42, the intermediate plate 41 and the counterplate 40, which engage in the axially extending internal toothing of the outer plate carrier 38.
  • the alignment member 60 on both sides corresponding to handle sections in the form of the radial flange 61 and the bent end 63 on the back plate 40 and the pressure plate 42 engage behind or over, so that an axial securing is given.
  • the directions axially, radially, tangentially and in the circumferential direction refer to the axis of rotation about which rotate the respective coupling, the coupling components such as discs, plates or the rotor of the electric machine.
  • the axial direction is orthogonal to the friction surfaces of the friction partners of the respective clutches.

Abstract

L'invention concerne un module hybride pour un groupe motopropulseur d'un véhicule automobile, comprenant un moteur électrique (6), un dispositif d'embrayage (9) et un embrayage de coupure (35). Cet embrayage de coupure (35) est couplé d'un côté à un volant bimasse (36) et de l'autre côté à un arbre intermédiaire (33) et présente un ensemble pouvant créer une liaison par friction comprenant un plateau de pression (40), un plateau de réaction (42) et au moins un plateau intermédiaire (41), ainsi que des disques d'embrayage (43, 44) en contact entre ceux-ci, le plateau de pression (42), le plateau intermédiaire (41) et les disques d'embrayage (43, 44) étant mobiles axialement. Il est prévu un support de disques extérieurs (38) qui est agencé solidement sur le volant bimasse (36) et auquel le plateau de réaction (40), le plateau intermédiaire (41) et le plateau de pression (42) sont accouplés de manière détachable, le plateau de réaction (40) étant accouplé solidaire en rotation et le plateau intermédiaire (41) et le plateau de pression (42) étant accouplés mobiles axialement au support de disques extérieurs (38). Les disques d'embrayage (43, 44) sont agencés mobiles axialement sur un support de disques intérieurs (80) qui est accouplé à l'arbre intermédiaire (33) solidaire en rotation et dans une position fixe axialement.
EP18746083.7A 2017-07-17 2018-07-11 Module hybride Withdrawn EP3655276A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102017116046 2017-07-17
DE102017130269.7A DE102017130269A1 (de) 2017-07-17 2017-12-18 Hybridmodul
PCT/DE2018/100629 WO2019015719A1 (fr) 2017-07-17 2018-07-11 Module hybride

Publications (1)

Publication Number Publication Date
EP3655276A1 true EP3655276A1 (fr) 2020-05-27

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ID=64745730

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18746083.7A Withdrawn EP3655276A1 (fr) 2017-07-17 2018-07-11 Module hybride

Country Status (5)

Country Link
EP (1) EP3655276A1 (fr)
KR (1) KR102648191B1 (fr)
CN (1) CN110914090B (fr)
DE (2) DE102017130269A1 (fr)
WO (1) WO2019015719A1 (fr)

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2803346B1 (fr) * 1999-12-30 2002-04-26 Valeo Embrayage double, en particulier pour vehicule automobile
WO2010081453A2 (fr) * 2009-01-19 2010-07-22 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Module hybride pour chaîne cinématique de véhicule
WO2011072653A1 (fr) * 2009-12-17 2011-06-23 Schaeffler Technologies Gmbh & Co. Kg Dispositif de transmission de couple de rotation
DE112012001990A5 (de) * 2011-05-05 2014-02-20 Schaeffler Technologies AG & Co. KG Drehmomentübertragungs-Vorrichtung
DE102011113326A1 (de) * 2011-09-14 2013-03-14 Daimler Ag Antriebsstrang für ein Hybridfahrzeug
DE102012201510A1 (de) * 2012-02-02 2013-08-08 Zf Friedrichshafen Ag Kupplungsanordnung
EP3123044B1 (fr) * 2014-03-27 2018-03-21 Schaeffler Technologies GmbH & Co. KG Plaque de pression et boîte de sécurité sous forme de composant commun
WO2015144171A2 (fr) * 2014-03-27 2015-10-01 Schaeffler Technologies AG & Co. KG Double embrayage à disques multiples
DE102014014669A1 (de) * 2014-10-02 2016-04-07 Borgwarner Inc. Drehmomentübertragungsvorrichtung und Antriebsstrang mit einer solchen Drehmomentübertragungsvorrichtung für ein Kraftfahrzeug
WO2017088869A1 (fr) * 2015-11-25 2017-06-01 Schaeffler Technologies AG & Co. KG Module hybride comprenant des embrayages de coupure et principal ainsi que des systèmes d'actionnement disposés entre ceux-ci

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Publication number Publication date
DE112018003644A5 (de) 2020-04-23
CN110914090B (zh) 2023-07-21
DE102017130269A1 (de) 2019-01-17
KR20200028394A (ko) 2020-03-16
CN110914090A (zh) 2020-03-24
WO2019015719A1 (fr) 2019-01-24
KR102648191B1 (ko) 2024-03-18

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