EP3899324A1 - Dispositif d'entraînement - Google Patents

Dispositif d'entraînement

Info

Publication number
EP3899324A1
EP3899324A1 EP19829467.0A EP19829467A EP3899324A1 EP 3899324 A1 EP3899324 A1 EP 3899324A1 EP 19829467 A EP19829467 A EP 19829467A EP 3899324 A1 EP3899324 A1 EP 3899324A1
Authority
EP
European Patent Office
Prior art keywords
output shaft
drive device
clutch
carrier
hydraulic
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Withdrawn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
EP19829467.0A
Other languages
German (de)
English (en)
Inventor
Matthew David HALL
Guido Schiedt
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.)
Audi AG
Original Assignee
Audi AG
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 Audi AG filed Critical Audi AG
Publication of EP3899324A1 publication Critical patent/EP3899324A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • F16D25/0638—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 with more than two discs, e.g. multiple lamellae
    • 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
    • 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
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/3023—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure
    • F16H63/3026—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure comprising friction clutches or brakes
    • 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
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/22—Vibration damping
    • 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 drive device with a drive unit having an output shaft, which is mechanically connected to an output shaft of the drive device via a clutch.
  • the publication US 2011/0294620 A1 is known from the prior art. This relates to a power transmission system for hybrid motor vehicles.
  • the document DE 815 151 B relates to a transmission for motor vehicles with a hydraulic torque wall ler and a planetary gear.
  • the drive device is used, for example, to drive a motor vehicle, to the extent that it is to provide a drive torque directed to drive the motor vehicle.
  • the drive device has the drive unit, which is configured, for example, as an internal combustion engine.
  • the drive unit is an electrical machine.
  • the drive unit has the output shaft, via which it provides the drive torque.
  • the output shaft is mechanically connected to the output shaft of the drive device, namely via the clutch. This means that the operative connection between the output shaft and the output shaft is either made or interrupted.
  • the clutch In a first switching position of the clutch, there is the effective connection between the output shaft and the output shaft, for example, the output shaft and the output shaft are rigidly coupled to one another when the first switching position of the clutch is present. In a second switching position of the clutch, however, the output shaft and the output shaft are decoupled from one another, in particular completely, so that no torque is transmitted between the output shaft and the output shaft or vice versa via the clutch.
  • the drive device From the drive shaft, the drive device provides the drive torque.
  • the output shaft is mechanically connected to at least one wheel axle of the motor vehicle and is at least temporarily or permanently operatively connected to it.
  • the output shaft is preferably permanently connected to a transmission, in particular a gear change transmission, of the drive device.
  • the Abtriebswel le can be mechanically connected to the wheel axle via the gearbox.
  • the clutch is a hydraulically operated clutch.
  • the actuator used to actuate the clutch should be at least partially integrated into the output shaft of the drive unit.
  • At least the hydraulic channel and the hydraulic cylinder are formed in the output shaft.
  • the hydraulic piston is arranged displaceably in the hydraulic cylinder.
  • the hydraulic piston is at least temporarily mechanically coupled to the clutch, so that the clutch can be actuated using the hydraulic piston. With different positions of the hydraulic piston within the hydraulic cylinder, there are different shift positions of the clutch, for example the first shift position or the second shift position.
  • the hydraulic channel opens into a hydraulic chamber, which is bounded jointly by a cylinder wall of the hydraulic cylinder and the hydraulic piston.
  • a hydraulic piston When the hydraulic piston is moved, the volume of the hydraulic chamber changes. Conversely, a change in the volume of the hydraulic chamber causes a displacement of the hydraulic piston in the hydraulic cylinder and thus an actuation of the clutch be.
  • a hydraulic fluid can be supplied to or removed from the hydraulic chamber via the hydraulic channel formed in the output shaft.
  • the hydraulic cylinder and thus the hydraulic chamber is connected via the hydraulic channel to a hydraulic pressure source, for example via a control valve, so that the desired switching position on the clutch can be set by specifically supplying and removing hydraulic fluid in or from the hydraulic cylinder.
  • a hydraulic pressure source for example via a control valve
  • the output shaft is mounted regionally in the output shaft. This means that the initial world le partially engages in the output shaft, for example with one of its ends.
  • the output shaft is mounted with respect to the output shaft so that it is ultimately mounted in the output shaft.
  • the output shaft can be mounted directly on the output shaft, for which purpose, for example, a bearing on the one hand on the output shaft and on the other hand on the drive shaft.
  • the output shaft is mounted only indirectly with respect to the output shaft, for example in that the output shaft is mounted with the aid of a first bearing on a housing of the drive device on which the output shaft is also mounted, namely by means of a second bearing.
  • the position of the output shaft in the output shaft achieves a particularly compact configuration of the drive device, in particular in the axial direction with respect to an axis of rotation of the output shaft or an axis of rotation of the output shaft.
  • a further embodiment of the invention provides that the output shaft is mounted on an intermediate shaft on and / or in the output shaft, the output shaft being coupled positively and / or non-positively to the intermediate shaft and the intermediate shaft being mounted in the output shaft by means of at least one bearing is. It has already been explained above that the output shaft can be mounted in regions in the output shaft. In addition, it is now clear that this bearing should be made via the intermediate shaft. This means that the output shaft is only mounted indirectly on the output shaft, namely via the intermediate shaft.
  • the output shaft is positively and / or non-positively connected to the intermediate shaft.
  • the positive connection can, for example, be made by means of a toothing of the output shaft which meshes with a counter toothing of the intermediate shaft in order to fix the output shaft and the intermediate shaft against one another at least in the circumferential direction.
  • the non-positive connection between the output shaft and the intermediate shaft can be established.
  • the non-positive connection is established by gear shaft is pushed in the axial direction to the intermediate shaft, so that a contact surface of the output shaft abuts against a mating contact surface of the intermediate shaft.
  • the intermediate shaft is mounted in and / or on the output shaft, namely via the at least one bearing.
  • the intermediate shaft can be mounted either directly or indirectly on the output shaft.
  • the intermediate shaft is rigidly or non-rotatably connected to the output shaft and rotatably ge directly on the output shaft.
  • the at least one bearing acts on the one hand on an outer circumferential surface of the intermediate shaft and on the other hand on an inner circumferential surface of the output shaft.
  • the at least one bearing is completely arranged in the output shaft, so that a further reduction in the installation space of the drive device is achieved.
  • a further embodiment of the invention provides that the intermediate shaft is fastened to the output shaft in the axial direction by means of a fastening element.
  • the intermediate shaft is positively attached to the output shaft using the fastening element.
  • the fastening element urges the intermediate shaft in the axial direction to the output shaft, namely in such a way that in the manner already described above, the contact surface on the mating contact surface is frictionally engaged.
  • the fastening element is, for example, in the form of a screw, the head of which is supported on an end face of the intermediate shaft, to which it is fastened with its thread on the output shaft or engages in it.
  • the fastening element completely penetrates the intermediate shaft in the axial direction.
  • the head of the fastening element viewed in the axial direction, is on the one hand the intermediate shaft and its thread is at least partially on the other hand the intermediate shaft.
  • Such a configuration represents a particularly permanent secure connection between the output shaft and the intermediate shaft.
  • a further development of the invention provides that the hydraulic channel in the output shaft on its side facing away from the hydraulic cylinder has an opening which is formed in a lateral surface of the output shaft.
  • the hydraulic channel opens on the one hand into the hydraulic chamber or the hydraulic cylinder and on the other hand passes through the outer surface of the output shaft, forming the mouth opening. Under the outer surface is to be understood from an outer peripheral surface of the output shaft.
  • the hydraulic channel has a first channel area and a second channel area, the first channel area on the one hand opening into the hydraulic cylinder and on the other hand merging into or opening into the second channel area.
  • the first channel region preferably runs straight throughout. For example, it runs parallel to the axis of rotation of the output shaft.
  • the second channel area opens into the first channel area and, on the other hand, passes through the lateral surface of the output shaft, forming the mouth opening.
  • the second channel area also preferably runs straight in and of itself.
  • the second channel region runs in the radial direction with respect to the axis of rotation of the output shaft, so that its longitudinal center axis intersects the axis of rotation.
  • the first channel area and the second channel area are each designed as a bore.
  • the first channel region is interrupted in the circumferential direction.
  • the first channel areas of these multiple hydraulic channels are, for example, formed discretely from one another and are spaced apart from one another in the circumferential direction. forward wave.
  • the second channel areas can be formed by a common annular chamber, which is formed through the outer surface of the outer surface. Such a continuous annular chamber in the circumferential direction ensures reliable loading of the hydraulic cylinder with hydraulic fluid or hydraulic fluid.
  • the intermediate shaft is coupled to at least one outer disk carrier of the clutch, in particular is designed in one piece and / or materially with it.
  • the outer plate carrier of the clutch is used for fastening at least one outer plate, which is provided and designed to interact with at least one inner plate of the clutch.
  • the at least one outer plate and the at least one inner plate are arranged with respect to one another in such a way that they can be displaced towards one another in the axial direction by means of the hydraulic piston and can thus be brought into frictional contact with one another.
  • a further embodiment of the invention provides that the Abtriebswel le is coupled to at least one inner disk carrier of the clutch, or at least partially forms the inner disk carrier.
  • the inner plate holder serves to hold the at least one inner plate. Due to the interaction of the inner plate and the outer plate, the inner plate carrier and the outer plate carrier can be non-positively coupled with one another, so that ultimately the output shaft and the output shaft can be non-positively coupled via the clutch.
  • the inner disk carrier is coupled to the output shaft. Loading however, it is particularly preferably formed by the output shaft. This enables a further reduction in the installation space of the drive device.
  • a Lamellenpa ket of the clutch has at least one outer disk connected to the outer disk carriers rotational test and at least one inner disk connected to the inner disk carrier rotational test and is arranged on a side of the outer disk carrier facing away from the output shaft.
  • the disk set of the clutch is composed of the at least one outer disk and the at least one inner disk. It is particularly preferred that a plurality of outer slats and a plurality of inner slats are provided, in particular the same number of outer slats as inner slats and vice versa.
  • the at least one outer plate is non-rotatably connected to the outer plate carrier, whereas the at least one inner plate is non-rotatably connected to the inner plate carrier.
  • the disk pack is now arranged on the side of the outer disk carrier facing away from the output shaft. This results in a direct connection to the inner disk carrier on the output shaft, so that an extremely compact drive device is present overall.
  • a further embodiment of the invention provides that a coupling element designed to actuate the plate pack acts on the one hand on the hydraulic piston and on the other hand on the plate pack and engages through the outer plate carrier.
  • the coupling element is used to establish an operative connection between the hydraulic piston and the plate pack.
  • the coupling element rests on the one hand on the hydraulic piston and on the other hand at least temporarily on the disk pack.
  • the coupling element is rigidly connected to the hydraulic piston or fastened to it. Because the disk pack is arranged on the side of the outer disk carrier facing away from the output shaft, the coupling element passes through the outer disk carrier in order to establish the operative connection between the hydraulic piston and the disk pack. As a result, the compact configuration of the drive device is implemented.
  • the outer plate carrier has a first carrier element and a second carrier element to form a vibration damper, the first carrier element being rigidly connected to the intermediate shaft and the second carrier element being connected in a rotationally fixed manner to the at least one outer plate and the first carrier element and the second Carrier element are connected to each other in an elastically damping manner.
  • the outer disk carrier is composed of at least the first Victoria element and the second carrier element.
  • the first carrier element is rigidly coupled to the intermediate shaft and the second carrier element is rotatably coupled to the outer lamella.
  • connection between the first and the second carrier element is elastic, in particular torsionally elastic, so that the first carrier element and the second Suele element in the circumferential direction with respect to the axis of rotation of the output shaft or the output shaft are elastically rotatable relative to each other.
  • the vibration damper is formed between the intermediate shaft and the disk set.
  • the vibration damper is completely integrated into the multi-plate clutch, in particular the vibration damper is at least partially in overlap with the plate set as seen in the axial direction.
  • the first carrier element and the second carrier element are connected to one another in an elastically damping manner in the circumferential direction by means of at least one damping element.
  • the damping element is, for example, in the form of a spring, in particular a helical spring.
  • the damping element encompasses the disk pack at least in regions in the circumferential direction and is particularly preferably in overlap with the latter, viewed in the axial direction.
  • a further drive unit is mechanically connected to the drive unit via the clutch.
  • the further drive gregat rigidly and / or permanently coupled to the output shaft.
  • the other drive unit is connected or connectable to the drive unit via the clutch and the vibration damper - if available.
  • the further drive unit is, for example, of a type which is different from the type of the drive unit.
  • the further drive unit can also be in the form of an internal combustion engine or an electrical machine. If the drive unit is in the form of an internal combustion engine, the further drive unit is particularly preferably configured as an electrical machine and vice versa. With the described configuration, a hybrid drive device is implemented in a particularly simple manner.
  • the further drive unit is arranged next to the drive unit, in particular axially parallel. While the drive unit has the output shaft, the further drive unit has another output shaft. The output shaft and the further output shaft are now not arranged coaxially to each other, but rather side by side, preferably in parallel.
  • the further drive unit is seen in the axial direction with respect to the axis of rotation of the output shaft at least partially or even completely in overlap with the drive unit.
  • the further drive unit has a smaller extension in the axial direction than the drive unit.
  • the further drive unit is particularly preferably connected via at least one gear stage to the output shaft of the drive device, in particular via a spur gear stage. This results in a particularly compact configuration of the drive device, in particular in the axial direction.
  • FIG. 1 shows a schematic illustration of a drive device with a drive unit and a further drive unit
  • Figure 2 is a schematic longitudinal sectional view through a clutch of the drive device
  • Figure 3 is a schematic detail longitudinal section through a
  • FIG. 1 shows a schematic illustration of a drive device 1, which has a first drive unit 2 and a second drive unit 3.
  • the first drive unit 2 is in the form of an internal combustion engine and the second drive unit 3 is in the form of an electrical machine.
  • the first drive unit 2 has a crankshaft, which serves as an output shaft 4.
  • At least one piston 5 of the first drive unit 2 engages on the output shaft 4 in a known manner.
  • the output shaft 4 of the first drive unit 2 is connected via a clutch 6 to an output shaft 7 of the drive device 1.
  • the output shaft 4 and the output shaft 7 are arranged coaxially to one another in the embodiment shown here Darge.
  • a gear wheel 8 is arranged on the output shaft 7 in at least one gear stage 9, via which the second drive unit 3 is mechanically connected to the output shaft 7, preferably rigidly and / or permanently.
  • a vibration damper 10 is integrated into the clutch 6 of the drive device 1. This means that the two drive units 2 and 3 are mechanically connected to one another via the clutch 6 and the vibration damper 10 and can thus be coupled to one another.
  • FIG. 2 shows a schematic longitudinal sectional view of the clutch 6 with the vibration damper 10 integrated therein. An intermediate shaft 11 can be seen, which is seen and designed for coupling to the output shaft 4.
  • the intermediate shaft 11 has a toothing 12, in particular an internal toothing, for coupling to the output shaft 4 or a counter toothing of the output shaft 4.
  • the intermediate shaft 11 by means of at least one bearing 13, in the exemplary embodiment shown here A plurality of bearings 13, in which the output shaft 7 is rotatably mounted, namely on the output shaft 7.
  • the bearing 13 lies on the inside on an outer circumferential surface of the intermediate shaft 11 and on the outside on an inner circumferential surface of the output shaft 7.
  • the intermediate shaft 11 is coupled to an outer disk carrier 14 of the clutch 6.
  • the outer disk carrier 14 has a first Reliefele element 15 and a second carrier element 16.
  • the first carrier element 15 is rigidly and permanently connected to the intermediate shaft 11, in particular the first rotary element 15 is formed in one piece and with the same material as the intermediate shaft 11.
  • the second support element 16 is connected to the first support element 15 in an elastically damping manner in the circumferential direction with respect to an axis of rotation 17 of the output shaft 7, namely via at least one damping element 18.
  • a plurality of damping elements 18 are spaced apart in the circumferential direction. However, there may also be only a single damping element 18.
  • the second carrier element 16 is connected in a rotationally fixed manner to at least one outer plate 19 of the clutch 6.
  • the clutch 6 has at least one inner plate 20 which is non-rotatably connected to an inner plate carrier 21.
  • the output shaft 7 serves as an inner disk carrier 21.
  • the at least one outer disk 19 and the at least one inner disk 20 together form a disk pack 22, which can be actuated, in particular compressible, to produce a connection between the intermediate shaft 11 and the output shaft 7.
  • the vibration damper 10 due to the integration of the vibration damper 10 in the clutch 6, a significant space saving can be achieved in the axial direction, in particular because the at least one damping element 18 and the disk set 22 are at least partially overlapping with one another in the axial direction.
  • the at least one damping element 18 at least partially encompasses the disk pack 22 in the circumferential direction.
  • the vibration damper 10 shown here is especially designed before trains in the manner of a dual mass flywheel.
  • FIG 3 shows a schematic longitudinal sectional view of a portion of the drive device 1, in particular the output shaft 4 of the first drive unit 2, the clutch 6 with the integrated vibration damper 10 and the output shaft 7 are shown. It can be seen that the output shaft 4 is fastened to the intermediate shaft 11 by means of a fastening element 23. In addition to the toothing 12, which produces a positive connection between the output shaft 4 and the output shaft 7, there is a non-positive connection between the output shaft 4 and the output shaft 7, which is realized with the aid of the fastening element 23.
  • the clutch 6 is actuated with the aid of an actuator 24, which has a hydraulic cylinder 25 formed in the output shaft 4 as well as hydraulic pistons 26 arranged in the hydraulic cylinder 25.
  • the hydraulic cylinder 25 and the hydraulic piston 26 together delimit a hydraulic chamber 27, into which a hydraulic channel 28 opens, which is also formed in the output shaft 4.
  • the hydraulic duct 28 has a first duct region 29 and a second duct region 30, the first duct region 29 opening directly into the hydraulic chamber 27, whereas the second Channel area 30 is connected to the hydraulic chamber 27 only indirectly via the first channel area 29.
  • the first channel region 29 preferably runs straight throughout. In particular, it runs parallel to the axis of rotation 17.
  • the second channel region 30 preferably also runs continuously straight, but can be perpendicular to the axis of rotation 7. It extends from the first channel region 29 in the radial direction to the outside. It can be provided that a plurality of hydraulic channels 28 are present, so that there are a plurality of first channel regions 29 spaced apart in the circumferential direction.
  • the second channel regions 30 can be designed as a continuous annular channel 31 in the circumferential direction. This is in flow connection with a flow opening 32 which is arranged in a bearing, in particular a sliding bearing. A region of the bearing can be seen, which represents, for example, a bearing bush 33 or a slip ring.
  • the bearing bush 33 lies close to an outer circumference of the output shaft 4, so that the hydraulic chamber 27 can be acted upon by hydraulic fluid 28 from the flow opening 32 with hydraulic fluid.
  • the described design of the drive device 1 has the advantage that it is extremely compact in the axial direction with respect to the axis of rotation 17, above all by integrating the vibration damper 10 into the clutch 6.
  • the clutch 6 is actuated with the aid of the actuator 24, which this has the hydraulic cylinder 25 and the hydraulic raulikkolben 26.
  • the hydraulic piston 26 is connected via a coupling element 34 to the disk set 22 of the clutch 6.
  • the coupling element 34 extends through the outer plate carrier 14, in particular the first carrier element 15 in the axial direction.
  • there is also a spring element 35 which engages on the one hand on the first carrier element 15 and on the other hand on the coupling element 34.
  • the spring element 35 urges the coupling element 34 in the direction of the hydraulic piston 26, in particular in such a way that the coupling element 35 bears against the hydraulic piston 26, preferably permanently. To this extent, the spring element 35 urges the coupling element 34 from the Plate pack 22 continues if the hydraulic piston 26 or the sen position allows this.
  • the spring element 35 can also be referred to as a return spring.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Arrangement Of Transmissions (AREA)

Abstract

L'invention concerne un dispositif d'entraînement doté d'un groupe motopropulseur (2) qui comprend un arbre de sortie qui est raccordé mécaniquement par un embrayage (6) à un arbre de sortie (7) du dispositif d'entraînement (1). Selon l'invention, au moins un canal hydraulique et un cylindre hydraulique relié au canal hydraulique (28) sont formés dans l'arbre de sortie. Un piston hydraulique (26) couplé à l'embrayage (6) pour son actionnement est disposé de manière déplaçable dans le cylindre hydraulique (25).
EP19829467.0A 2018-12-20 2019-12-13 Dispositif d'entraînement Withdrawn EP3899324A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018222514.1A DE102018222514B4 (de) 2018-12-20 2018-12-20 Antriebseinrichtung
PCT/EP2019/085038 WO2020126886A1 (fr) 2018-12-20 2019-12-13 Dispositif d'entraînement

Publications (1)

Publication Number Publication Date
EP3899324A1 true EP3899324A1 (fr) 2021-10-27

Family

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Application Number Title Priority Date Filing Date
EP19829467.0A Withdrawn EP3899324A1 (fr) 2018-12-20 2019-12-13 Dispositif d'entraînement

Country Status (5)

Country Link
US (1) US11466734B2 (fr)
EP (1) EP3899324A1 (fr)
CN (1) CN113167379B (fr)
DE (1) DE102018222514B4 (fr)
WO (1) WO2020126886A1 (fr)

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE815151C (de) * 1948-07-31 1951-09-27 Gen Motors Corp Kraftuebertragungsgetriebe fuer Motorfahrzeuge mit einem hydraulischen Drehmomentwandler und einem Umlaufraedergetriebe
DE3711490C2 (de) * 1986-04-16 1995-04-13 Volkswagen Ag Gangschalteinrichtung
DE3838865A1 (de) 1987-12-19 1989-06-29 Luk Lamellen & Kupplungsbau Mehrfachkupplungsaggregat
US5158582A (en) 1988-05-30 1992-10-27 Hitachi Zosen Corporation Method of removing NOx by adsorption, NOx adsorbent and apparatus for purifying NOx-containing gas
US5057128A (en) 1990-07-03 1991-10-15 Flakt, Inc. Rotary adsorption assembly
DE19833378A1 (de) * 1998-07-24 1999-12-09 Getrag Getriebe Zahnrad Doppelkupplung
US6443286B1 (en) * 2001-01-18 2002-09-03 Twin Disc, Incorporated Modulatable power transmission clutch and a marine transmission
KR100598843B1 (ko) 2003-12-10 2006-07-11 현대자동차주식회사 비틀림 진동 댐퍼
DE102010052384A1 (de) * 2009-11-24 2011-05-26 Schaeffler Technologies Gmbh & Co. Kg Drehmomentübertagungseinrichtung
JP5533247B2 (ja) * 2010-05-20 2014-06-25 日産自動車株式会社 駆動力伝達装置
WO2011150297A2 (fr) 2010-05-26 2011-12-01 Ares Transportation Technologies Système de transmission de force motrice pour véhicule hybride
DE102012223950B4 (de) * 2012-01-20 2018-10-25 Schaeffler Technologies AG & Co. KG Übertragungseinheit mit integriertem Dämpfersystem
DE112014001701A5 (de) * 2013-03-26 2015-12-17 Schaeffler Technologies AG & Co. KG Lagerung und axiale Abstützung einer Doppelkupplung an einer Getriebeeingangswelle
WO2017067554A1 (fr) * 2015-10-22 2017-04-27 Schaeffler Technologies AG & Co. KG Amortisseur de vibrations de torsion et groupe propulseur hybride
DE102015220596A1 (de) * 2015-10-22 2017-04-27 Schaeffler Technologies AG & Co. KG Kupplungs-Drehschwingungsdämpfer-Zusammenbau mit einer in einem Drehteil eines Drehschwingungsdämpfers integrierte Hybridtrennkupplung
DE102015221368B4 (de) * 2015-11-02 2018-01-11 Bayerische Motoren Werke Aktiengesellschaft Abkoppelungseinrichtung Verbrennungsmotor PHEV-Getriebe
KR101952084B1 (ko) * 2015-11-25 2019-02-25 섀플러 테크놀로지스 아게 운트 코. 카게 분리 클러치 및 주 클러치, 그리고 이들 사이에 배치된 작동 시스템을 포함하는 하이브리드 모듈
JP6663760B2 (ja) * 2016-03-18 2020-03-13 株式会社エクセディ トルクコンバータ
FR3058098B1 (fr) * 2016-10-27 2024-01-19 Valeo Embrayages Dispositif de transmission pour vehicule hybride
JP6531133B2 (ja) * 2017-04-27 2019-06-12 本田技研工業株式会社 ハイブリッド車両の駆動装置

Also Published As

Publication number Publication date
DE102018222514A1 (de) 2020-06-25
DE102018222514B4 (de) 2022-08-04
US20210396277A1 (en) 2021-12-23
WO2020126886A1 (fr) 2020-06-25
US11466734B2 (en) 2022-10-11
CN113167379A (zh) 2021-07-23
CN113167379B (zh) 2022-12-09

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