CN109689411A - Hybrid powertrain with intermediate gear - Google Patents

Hybrid powertrain with intermediate gear Download PDF

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Publication number
CN109689411A
CN109689411A CN201780054339.1A CN201780054339A CN109689411A CN 109689411 A CN109689411 A CN 109689411A CN 201780054339 A CN201780054339 A CN 201780054339A CN 109689411 A CN109689411 A CN 109689411A
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CN
China
Prior art keywords
gear
powertrain
torque
sub
motor
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Granted
Application number
CN201780054339.1A
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Chinese (zh)
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CN109689411B (en
Inventor
马丁·福内赫姆
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Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Publication of CN109689411A publication Critical patent/CN109689411A/en
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Publication of CN109689411B publication Critical patent/CN109689411B/en
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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
    • B60K6/42—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
    • 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
    • B60K6/36—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 transmission gearings
    • 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
    • B60K6/36—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 transmission gearings
    • B60K6/365—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 transmission gearings with the gears having orbital motion
    • 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
    • B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
    • B60K6/54—Transmission for changing ratio
    • B60K6/547—Transmission for changing ratio the transmission being a stepped gearing
    • 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
    • B60K2006/4833—Step up or reduction gearing driving generator, e.g. to operate generator in most efficient speed range
    • B60K2006/4841—Step up or reduction gearing driving generator, e.g. to operate generator in most efficient speed range the gear provides shifting between multiple ratios
    • 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/093—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts
    • F16H2003/0931—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears with two or more countershafts each countershaft having an output gear meshing with a single common gear on the output shaft
    • 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

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Hybrid Electric Vehicles (AREA)

Abstract

The invention relates to a hybrid drive train (1) having a first partial drive train (2) which can be driven by an internal combustion engine and a second partial drive train (3) which can be driven by an electric motor, wherein the first partial drive train (2) comprises a first transmission and the second partial drive train (3) comprises a second transmission which is designed as a planetary gear (12), wherein a torque of the first partial drive train (2) can be transmitted to an output shaft gear (4) either via the first transmission or via an intermediate wheel (15) which can be frictionally coupled to the first partial drive train (2), and wherein a torque of the second partial drive train (3) can be transmitted to the output shaft gear (4) via a planet carrier (35) of the planetary gear (12) and the intermediate wheel (15), wherein the geometric arrangement of the planetary gear (12) is selected, so that the torque generated by the electric motor can be transmitted via the ring gear (31) of the planetary gear (12).

Description

Hybrid powertrain with middle apron
Technical field
The present invention relates to a kind of hybrid powertrain, with preferred internal combustion engine it is directly drivable/directly drive First sub- powertrain and preferred motor be directly drivable/the second sub- powertrain for directly driving, wherein described First sub- powertrain includes the first speed changer and the second sub- powertrain includes be configured to epicyclic transmission mechanism Two speed changers, wherein the torque of the first sub- powertrain can or via the first speed changer or via with first The sub- powertrain breast wheel coupled that can rub is transmitted on output shaft gear, that is, is transmitted to and output shaft is to transmit torque On the gear that mode connects, and wherein planet carrier and centre of the torque of the second sub- powertrain by epicyclic transmission mechanism Wheel is transmitted on output shaft gear.
Background technique
A kind of hybrid powertrain for motor vehicles known, hybrid vehicle from WO2014/006016A1 And its application.Hybrid powertrain disclosed herein includes internal combustion engine and connects with power electric device and energy storage The motor connect, motor energy torque transmitting ground are connected with output shaft.Hybrid powertrain is characterized in that, the internal combustion engine Output shaft and the output shaft of the motor carry multiple output shaft pinion gears respectively, the output shaft pinion gear is respectively with first The line shaft pinion gear of line shaft engages, and first line shaft is spaced apart with output shaft to be arranged and couple with driven shaft, the output Axis pinion gear and/or line shaft pinion gear pass through changeable shape and cooperate coupling individually axis connection associated with difference, Wherein the output shaft of the internal combustion engine is rigidly connect with internal combustion engine, is coupled without shape cooperation or force-fitting.
10 2,014 222 587 A1 of DE discloses a kind of hybrid powertrain for motor vehicles, has interior Combustion engine and motor connect with power electric device and energy storage, with stator and rotor, the motor can torque transmitting Ground and driven axis connection, wherein internal combustion engine is coupled with the internal combustion engine drive shaft for carrying one or more drive shaft pinion gears, motor Rotor via the planetary set for including sun gear, fishplate bar and gear ring and carry the motor drivens of one or more drive shaft pinion gears Axis couples, in the fishplate bar and gear ring the element output element of another element as planetary set as input element, Wherein rotor can selectively be connect by changeable clutch with the output element of input element or the planetary set, motor Drive shaft and internal combustion engine drive shaft can be connected to each other by changeable spindle clutch, at least one drive of internal combustion engine drive shaft Corresponding with the first line shaft the line shaft pinion gear of moving axis pinion gear forms the pinion gear pair for switchably transmitting torque, and described first It is coupled with driven shaft to line shaft transmitting torque, and at least one drive shaft pinion gear of motor driving shaft is corresponding with line shaft Line shaft pinion gear forms the pinion gear pair of transmitting torque, couples with driven shaft to the line shaft transmitting torque.
Be formed as controllable multiplate clutch furthermore there is disclosed spindle clutch, and internal combustion engine by freewheel with Internal combustion engine drive shaft couples.
Other hybrid powertrains for example from 10 2,012 016 988 A1 of DE, 2014/0352491 A1 of US and It is known in 2015/0298535 A1 of US.
The hybrid powertrain of the prior art has the drawback that they need relatively large structure space, especially dynamic The part for being arranged in wheel side of power power train.
Summary of the invention
The purpose of the present invention is avoiding or at least mitigating the prior art, especially it is in the structure space of wheel side Motor provides significantly more space, is arranged other within this space with drive shaft out-of-alignment axis and its gear to clock In shape structure space, this needs the transmission parts constructed especially shortly.
The purpose of the present invention is accomplished in that the geometry of epicyclic transmission mechanism in such hybrid powertrain Setting is selected as so that torque caused by motor by the gear ring of epicyclic transmission mechanism can transport to/be delivered to second son Powertrain.
Advantageous embodiment is claimed in the dependent claims and is described below.
It is therefore advantageous that the first sub- powertrain and the second sub- powertrain transmit torsion can rub with coupling The mode of square is connected to each other, and the epicyclic transmission mechanism (12) and first son is spatially arranged in friction clutch Between powertrain (2).This is important particularly with " the generator operation " of motor, because in this way can will be by internal combustion The torque that machine generates is conveyed to motor, and the motor can be by the mechanical switch for being conveyed to it in this way at being stored in battery In electric energy.
Also, it has proven that the gear type has grade advantageously, the first transmission configuration is that gear type has a grade transmission mechanism Transmission mechanism has the gear being arranged in first (tooth) wheel plane and second (tooth) wheel plane.
In order to save space, it is advantageous to which the transmission ratio (digitally) of breast wheel is located at from first round plane to the second wheel It is poor that two transmission ratios are divided into the transmission ratio difference of plane and by the difference.
It is verified that advantageously, first round plane corresponds to 1 gear and 2 gears, the second wheel plane corresponds to 4 gears and 5 gears, and And breast wheel forms third round plane and corresponds to 3 gears.
Furthermore it is advantageous that the first speed changer have to the first jackshaft at least two changeable transmission ratios and With the changeable transmission ratio of at least two to the second jackshaft.
It having been demonstrated to be advantageous thus, axis is arranged to, so that from the input shaft of the described first sub- powertrain, Angle between first jackshaft and the second jackshaft is 85 ° to 87 °, and from output shaft, among described first Angle between axis and the second jackshaft is 61 ° to 63 °, from the jackshaft, the input shaft and the output shaft it Between angle be 102 ° to 112 °, and the central point of the breast wheel is located at connection between the input shaft and output shaft Line as on downside: be located on the side with the jackshaft of first gear.
It is also advantageous that in order to which motor or motor/electric drive torque to be transmitted on output shaft, it is used Epicyclic transmission mechanism is at least partially situated at the internal rotor of electric drive.
In order to transmit torque caused by motor, it has been found that advantageously, the transmitting can pass through epicyclic transmission mechanism Sun part can be connect with shell in a manner of changeable or with another connecting pin of epicyclic transmission mechanism to switch.
Advantageously, the transmission ratio of breast wheel is sufficiently large, so that pure electrically actuated and reverse travel is possible, and enough It is small, so that motor can satisfy the tractive force in the shift process of internal combustion engine when up to the speed of about 100km/h Gap.
In addition, the invention also includes hybrid powertrains according to the present invention from second gear (2 gear) to middle apron (3 gear) Shift transformation method or working method, have follow steps: reducing the torque that internal combustion engine generates, while improving motor The torque of generation；When sliding sleeve is not by pulling force, sliding sleeve is removed from second gear；Make the revolving speed of internal combustion engine towards third The rotating speed of target of gear reduces (adjusting)；By the friction clutch engagement in the torque stream of breast wheel, and it is bonded on when necessary Clutch at internal combustion engine, wherein then according to battery status, carry out step 1 torque direction and sequence it is complete or partial It reverses.
In other words, the invention reside in hybrid powertrain is configured to, by the wheel side or the tyre side that increase transmission mechanism On structure space mode, bigger structure space can be provided for motor.For this purpose, at least first and second wheel planes are for extremely Few four transmission ratios.By the breast wheel in the transmission plane of the differential mechanism of hybrid vehicle, intermediate transmission ratio is set.In this Between transmission ratio be used for hybrid vehicle electric drive mode and combination drive mode.For this purpose, motor passes through epicyclic transmission mechanism It is connect with breast wheel.Motor is connect by the internal gear of epicyclic transmission mechanism and the planet carrier of epicyclic transmission mechanism with breast wheel. Preferably, the first separation clutch is arranged between internal combustion engine and drive shaft.It is further preferred that being replaced to the first separation clutch Generation or addedly, second separation clutch be arranged between internal combustion engine and breast wheel.
It can also be said that the present invention includes a kind of hybrid power transmission mechanism, plurality of power train combination is on differential mechanism Big final driving wheel on.Here, oil-engine driven sub- powertrain is located at as axial very short transmission mechanism The internal combustion engine side of final driving plane, and there are two other axis, (having can cut tool other than input shaft (with gear) The gear changed) and breast wheel, so that obtaining the teeth portion that a total of three is engaged with differential mechanism.It is passed in oil-engine driven sub- power In two gear planes of dynamic system, each three gears (i.e. the gear of the gear of input shaft and jackshaft) with saving structure space that This engagement, so that four kinds of transmission ratios are obtained, wherein the difference from a gear plane to another gear plane is disadvantageously big. In hybrid power transmission mechanism according to the present invention, the maximum gear difference expand (for example, being expanded to 2 to 2.5) at so that Another transmission ratio fills gear gap as middle apron, thus formed two acceptable gears it is poor (such as 1.4 to 1.6, radical sign 2 to 2.5).Here, middle apron is realized by another gear (breast wheel) in final driving wheel plane and e.g. third gear (3 gear), and four transmission ratios above-mentioned form 1 gear, 2 gears, 4 gears and 5 gears.
The sub- powertrain of motor drive occupies the tyre side of final driving plane together with motor or motor Axial longer structure space, and including changeable when necessary planetary stage and connecting element, so as to via above-mentioned breast wheel It is effectively connect with intermediate gearing with differential mechanism.To this end it is advantageous that middle apron is third gear, and therefore from internal combustion engine There is also two lower transmission ratios and at least two higher transmission ratios from the point of view of angle.Therefore transmission ratio is sufficiently large, so that electric Motivation generates the tractive force (usually 2500Nm vehicle bridge torque) for being sufficient to electric activation and reverse travel together with planetary stage. However transmission ratio is also sufficiently small simultaneously so that until about 100km/h speed when motor together with planetary stage not yet Reach its rev limit, and then fills up tractive force gap in the possible shift transformation of internal combustion engine.
Thus, it has proved that advantageously, the motor of wheel side setting is coaxially disposed with crankshaft, preferably as internal rotor Setting.It is coaxially feasible, but the power of limiting motor with breast wheel, because the outer diameter of motor does not allow and differential mechanism and side Axis collides and does not allow to collide with jackshaft.
Detailed description of the invention
The present invention is explained in greater detail below by way of attached drawing, different embodiments is shown in attached drawing.In figure:
Fig. 1 shows the diagram of the logical construction of hybrid powertrain according to the present invention；
Fig. 2 shows the schematic diagrames of the space of axis included in hybrid powertrain setting；
Fig. 3 shows the shift figure and gear or driving mode of hybrid powertrain；
Fig. 4 shows the schematic diagram of the geometry of the hybrid powertrain in the first illustrative embodiments；
Fig. 5 shows the first illustrative embodiments and positioning of friction clutch；
Fig. 6 shows the second illustrative embodiments and positioning of friction clutch；
Fig. 7 shows the third illustrative embodiments and positioning of friction clutch；
Fig. 8 shows the first exemplary setting of epicyclic transmission mechanism, and wherein sun gear can be connect with shell；
Fig. 9 shows the second illustrative embodiments of epicyclic transmission mechanism, and wherein planetary set is lockable.
Figure 10 shows the illustrative embodiments of planetary set, wherein the torque generated by motor is transmitted to (row from gear ring Star) on frame；
Figure 11 shows an illustrative embodiments, and wherein planetary set is locked up and is directly passed by the torque that motor generates It is delivered on load-bearing part；
Figure 12 shows the possible exemplary implementation of the input shaft for internal combustion engine to be connected to the first sub- powertrain Mode；
Figure 13 shows the first illustrative embodiments of the geared system of first round plane；
Figure 14 shows the illustrative embodiments of the geared system of the second wheel plane；
Figure 15 shows the illustrative embodiments of the geared system of third round plane；
Figure 16 shows the illustrative embodiments of the geared system of the entire first sub- powertrain and output shaft；
Figure 17 shows the first illustrative embodiments of the bearing of breast wheel；
Figure 18 shows the second illustrative embodiments of the bearing of breast wheel；
Figure 19 shows the third illustrative embodiments of the bearing of breast wheel；
Figure 20 shows the flow chart from 2 gears to the shift of 3 gears；
Figure 21 shows the flow chart from 4 gears to the shift of 5 gears；
Figure 22 shows the flow chart for controlling engine start during pure electricity traveling；With
Figure 23 shows the flow chart of each step of engine start in the flow chart of Figure 22.
These figures are only schematical and are only used for understanding the present invention.Identical element is equipped with identical attached drawing mark Note.
Specific embodiment
The feature of each embodiment can also be realized in other embodiments.So they can be interchanged.
Fig. 1 shows the summary view of the logical construction form of hybrid powertrain 1, and the hybrid powertrain is by two Sub- powertrain 2,3 is constituted, and the sub- powertrain can be connect in a manner of transmitting torque respectively with output shaft gear 4. In illustrative embodiments shown here, output shaft gear 4 is constituted in the form of so-called final driving wheel 5, this is final Driving wheel is fixed on differential mechanism 6.By differential mechanism 6, the torque to get there is distributed and is transmitted on wheel 7.Sub- power passes Dynamic is that 2 can also be referred to as the first sub- powertrain 2, and driven in the example embodiment shown in fig. 1 by internal combustion engine 8 It is dynamic.
The first sub- powertrain 2 be arranged on the side of final driving plane as very short transmission mechanism and It (is seen description herein below) with multiple gears, the final locator qualification for driving plane by final driving wheel, by described Four different transmission ratios may be implemented in gear.Gear is arranged in herein in two (tooth) wheel planes, i.e. first round plane 9 and Two wheel planes 10, one of wheel plane is associated with 1 gear and 2 gears, and another wheel plane is associated with 4 gears and 5 gears.
The sub- powertrain 3 that can also be used as the second sub- powertrain 3 passes through such as motor drive of motor 11 simultaneously And including epicyclic transmission mechanism 12.Second sub- powertrain 3 is located on the other side of final driving plane, which can also With referred to as tyre side 13.Side where first sub- powertrain 2 of final driving plane is referred to as internal combustion engine side 14. Second sub- powertrain 3 connects in such a way that breast wheel 15 can transmit torque with output shaft gear 4, breast wheel setting In third round plane 16.Plane equipped with epicyclic transmission mechanism 12 is also referred to as planet plane 17.
Pass through clutch 18 and first in the illustrative embodiments for the hybrid powertrain 1 that internal combustion engine 8 is shown here Sub- powertrain 2 connects.Alternatively, internal combustion engine 8 can also directly with the input shaft 19 of the first sub- powertrain 2 (referring to Fig. 4) connect.In addition, the first sub- powertrain 2 can be by clutch 20 and breast wheel 15 and then with output shaft gear 4 to pass The mode of torque delivery connects.
Fig. 2 shows the setting of the space of the axis of hybrid powertrain 1, medium and small black circles mark the contact of gear Torque occurs at these contact points for point from the transmitting on an axis to another axis.
Fig. 3 shows the shift figure of hybrid powertrain 1.Here, can be realized by hybrid powertrain 1 for each Gear, the position of shift clutch collar S is shown, shift engagement be set on first round plane 9 and second take turns plane 10 it Between jackshaft 23,24 (referring to fig. 4) on and by be moved to the left or right can with first round plane 9 be associated with gear or The association gear that person second takes turns plane 10 is connected in a manner of transmitting torque.If sliding sleeve S is not engaged with any gear, Then it is in so-called neutral gear position N.
The S in Fig. 31N4Refer to such as lower slipping sleeve, be arranged on the first jackshaft 23 and realize first by mobile Keep off the transmission ratio of (first round plane 9) or the transmission ratio of fourth gear (the second wheel plane 10).As sliding sleeve S1N4Not and One or second wheel plane 9,10 in gear engagement when, sliding sleeve S1N4In neutral gear position N.S2N5Indicate Fig. 3 in as Lower slipping sleeve is arranged on the second jackshaft 24 and similar to sliding sleeve S1N4Realize second gear (first round plane 9) in ground Or fifth gear (the second wheel plane 10).
Shift gears clutch collar S2N5Also can take up neutral gear position N, wherein it neither in first round plane 9 gear nor It is engaged with the gear in the second wheel plane 10.
Typically for shifting element it is contemplated that any structure type and mode of operation, the reality of especially axial short structure Apply scheme.
In addition to sliding sleeve S1N4、S2N5Position, whether the shift figure in Fig. 3 also illustrate clutch 20 (K in Fig. 3) It is transmitted for torque, i.e., in this case, torque is transmitted via clutch 20 by frictional fit and (uses " 1 " table in Fig. 3 Show) or do not transmit torque (being indicated in Fig. 3 with " 0 "), which is arranged on the described first sub- powertrain 2 and second Between sub- powertrain 3 and it is preferably configured as the form of friction clutch, such as multidisc clutch.In addition it also gives Shift gears clutch collar SHNLPosition, the shift clutch collar switch epicyclic transmission mechanism 12 transmission ratio." L ", " H " and " N " herein Refer to three kinds of possibilities using motor, wherein " L " corresponds to low speed and high transmission ratio, " H " corresponds to high speed, wherein planet Group is locked (that is, the transmission ratio on the torque from motor to the second sub- powertrain 3 is equal to 1), and wherein " N " table Show unused motor.
The gearshift S of the transmission ratio of two pure electricityHNLIt is arranged by the structural detail of friction or shape cooperation in driver In the tyre side 13 of structure, advantageously at least partly it is arranged in the rotor of motor 11.The gearshift with shell by fixing , preferably electromechanical actuator operation.
This meaning can also be transferred on the label in different gears.Therefore, for keeping off ICE1 to ICE5 (ICE= "Internal Combustion Engine"；Internal combustion engine) each of have three kinds of sides that can be combined using motor respectively Case.Traveling of reversing gear (gear " R " in Fig. 3) and the starting (" E in Fig. 3H") it is pure electricity ground (E=" electricity "；EM=is " electronic Machine "；The motor or electric notor of electricity) it realizes.
In addition, also showed that in Fig. 3 internal combustion engine 8 corresponding to the transmission ratio (transmission ratio ICE) of corresponding gear and electronic The transmission ratio (transmission ratio EM) corresponding to corresponding gear of machine 11.
Fig. 4 shows the exemplary geometric structure of hybrid drive train 1.What the first sub- powertrain 2 was shown here at Include: input shaft 19 in illustrative embodiments, be arranged on the input shaft two gears 21,22 as fixed gears (that is, with The gear that input shaft 19 is fixedly connected), and two gears have different diameters；With the first jackshaft 23 and the second jackshaft 24, two gears 25,26 or 27,28 with different-diameter are respectively set on it as free gear (that is, these gears are borrowed It helps sleeve to be arranged on corresponding jackshaft 23,24, realizes that torque is passed by the way that sliding sleeve is engaged corresponding free gear It passs, which is not shown here).Here, gear 21,25 and 27 forms first round plane 9, the formation of gear 22,26 and 28 Second wheel plane 10.Each jackshaft 23,24 has gear 29 or 30 on end, and gear 29 or 30 is nibbled with output shaft gear 4 It closes.Gear 29 is shown by dotted arrow in the figure with engaging for output shaft gear 4.Second sub- powertrain 2 includes planet Transmission mechanism 12, with gear ring 31, planetary gear 32 and with the solar shaft 33 of sun gear 34.In this case, planet carrier 35 are partially formed to clutch 20 and have gear 44 on its axial end portion away from planetary gear 32, and the gear 44 is in Between wheel 15 engagement.Therefore, epicyclic transmission mechanism 12 is by the torque from motor 11 via gear ring 31, planetary gear 32 and planet carrier 35 It is transmitted on breast wheel 15, which engages with output shaft gear 4.Solar shaft 33 (and therefore sun gear 34) is in the implementation Be formed as fixing element in mode and be supported in shell 37 via support component 36.
Support component 36 can for example be configured to tool in the case, and there are three position " H ", and " N ", " L " (sees also Fig. 3) Shift clutch collar SHNL, wherein H corresponds to the drive range (see Figure 11) that planetary set is locked, thus epicyclic transmission mechanism 12 Transmission ratio be equal to 1；N corresponds to the neutral for not transmitting the torque of motor, and L corresponds to the position for realizing high transmission ratio.L Preferably selected in low speed, and H is more likely to the use in high speed.
Alternatively, support component 36 also can be implemented only two drive ranges " N " and " L " (N was used as torsion to protect), and It is embodied as changeable brake in reduced form or is embodied as sun part (preferably in the planetary set of small speed ratio) forever Long housing support.Support component 36 and the possible executive device to this are advantageously placed in hybrid powertrain In 1 tyre side 13 (rightmost side in the figure).
As shown here, clutch 20 can be placed in the structure space of wheel side or optionally or in being placed on In the structure space of combustion engine side.Under any circumstance, clutch 20 is all located at a left side for epicyclic transmission mechanism 12 or planet plane 17 Side.
Epicyclic transmission mechanism 12 is advantageously disposed in the rotor (not shown) of motor 11, but optionally, if wheel side Structure space in there are sufficient spaces, then can also be axially disposed at the side of motor 11.
Fig. 5 to Fig. 7 shows the different illustrative embodiments of clutch 20.So implementation as shown here of clutch 20 It is configured to friction clutch, such as the form of multidisc clutch in example, and the structure for being located at wheel side in fig. 5 and fig. is empty Between in, and in Fig. 7 positioned at internal combustion engine side structure space in.If clutch 20 is arranged in the structure space of wheel side, So it is advantageously located at (referring to Fig. 5) completely, but is located at the rotor of motor 11 (here not (referring to Fig. 6) at least partially It is explicitly illustrated) within.In this case, the clutch for example can relative to epicyclic transmission mechanism 12 planet carrier 35 with tie It neighbouring mode or is constituted in a manner of Component composition on structure.In embodiment as shown in Figure 5 and Figure 6, clutch 20 is located at Between third round plane 16 and planet plane 17, and the second wheel plane 10 and third round are set in the embodiment shown in fig. 7 Between plane 16.As the substitution of Fig. 7, clutch 20 can be placed in third round plane 16 in internal combustion engine side 14.
For the reason of the structure space, clutch 20 is arranged in the rotor (not shown) of motor 11 and is advantageous.But When being that space is enough in the structure space for taking turns side, it can also axially implement clutch 20 beside motor 11.In clutch 20 are arranged when in tyre side 13, and clutch 20 is connect via hollow shaft with 3 gears (middle apron).Particularly advantageously, clutch 20 It is dry type or wet-type multi-disc clutch.
The preferred electromechanical ground of the actuating of clutch 20 is for example by the lever of motor drive, pull rod/pressure of motor drive Bar is realized, or is realized as follows: the mechanism and axial bearing of motor operation may be non-linearly driven, rotation or translation. It as an alternative, can also be hydraulically by slave cylinder with pressure-control valve or by with the rotation of axial bearing or static Pressure chamber realizes the actuating.It is also conceivable to hydrostatic-electronic (electro-hydraulic) actuator, such as motor drive Hydraulic pump or hydraulic piston with axial bearing.The component of actuation means is at least partially disposed on motor on geometry In 11.
Fig. 8 and 9 shows showing for the support component 36 of changeable brake 38 (Fig. 8) or gearshift 39 (Fig. 9) form Example property embodiment.Support component 36 is advantageously separable relative to transmission mechanism shell 37.It is possible thereby to protect at high vehicle speeds Motor 11 is protected from high revolving speed.Support component 36 is shown here in Fig. 8, consists of changeable brake 38, in which: static Sliding sleeve 40 can be in right shift to (synchronous when necessary) shift teeth portion 46, (and the thus sun of solar shaft 33 as a result, Wheel is 34) fixed.
If solar shaft 33 is not only separable but also changeable (see Fig. 9), it is particularly advantageous.Switching 39 is in such as Fig. 8 The support function of middle realization (is connect with shell；The right positions of the corresponding sliding sleeve 40 in Fig. 9) and so-called lock function It is carried out between (leftward position of sliding sleeve 46 in corresponding diagram 9), support component 36 and gear ring 31 connect in the lock function It connects, thus the transmission ratio of epicyclic transmission mechanism 12 is equal to 1.
Not only motor 11 by separation is protected against high revolving speed as a result, but also even if motor is still at high vehicle speeds It so can produce tractive force or thrust.The embodiment shown in Fig. 9 shows the sliding sleeve rotated together with solar shaft 33 40, which can be moved to the right (when necessary synchronously) on fixed teeth portion (being similar to brake 38).As an alternative, Sliding sleeve 40 (when necessary synchronously) can be moved to the left in the shift teeth portion rotated together with gear ring 31, thus planetary set It is locked.It means that there is no relative motion between gear ring 31, planetary gear 32 and solar shaft 33 or sun gear 34, and come from Motor 11 or the torque for being provided by it or generating directly pass through planet carrier 35 and are transmitted on output shaft gear 4.
Sliding sleeve 40 is for example operated by selector fork or by the bearing of transmitting axial movement.For this actuating Device is preferably electromechanical or hydrostatic and is located on transmission mechanism shell 37.
Figure 10 and 11 shows the illustrative embodiments of epicyclic transmission mechanism 12.Epicyclic transmission mechanism 12 for taking turns side setting Advantageously cause from 1.5 to 2.2 transmission ratio of motor torque according to the size of motor 11, which for example may be configured as (high Performance) form of motor, this obtains 6.1 to 9 total transmission together with transmission ratio between breast wheel 15 and differential mechanism 6 Than.
Epicyclic transmission mechanism 12 connects into thus, so that sun part 33,34 (such as changeable) be braked (referring to figure 10), the gear ring 31 is driven by motor 11 and planet carrier 35 is connect with breast wheel 15.Here, gear ring 31 advantageously generates The radially nested structural unit with the rotor (not shown) of motor 11.
In the connection, cause the epicyclic transmission mechanism 12 of desired transmission ratio for example with following characteristics/value: sun tooth The number of teeth=70 of wheel 34, the number of teeth=110 of gear ring 31；The number of teeth=20 of planetary gear 32, plurality of (small) planetary member 32 are distributed On ring week.Alternatively, epicyclic transmission mechanism 12 can have the number of teeth 56 of sun gear 34, the number of teeth 84 of gear ring 31 and planetary gear The 14 of 32 number of teeth, wherein same multiple (small) planetary members were distributed on ring week.
Figure 11 shows the epicyclic transmission mechanism 12 in the lock state that such as Fig. 9 has been described, wherein the motor 11 Torque directly (transmission ratio is equal to 1) is transferred to planet carrier 35, and is therefore transmitted on breast wheel 15.
Figure 12 shows the possible illustrative embodiments for being coupled to internal combustion engine 8 in first sub- powertrain 2. This input shaft 19 and internal combustion engine 8 connection via torsional vibration damper 41 known per se, such as in flywheel or double mass flywheel Form torsional vibration damper carry out.Other structures member can be advantageously placed between torsional vibration damper 41 and input shaft 19 Part, can also be in such a way that serial or parallel connection combines.Such as freewheel for navigating by water function, with the changeable of actuator Freewheel, the friction clutch with actuator, the dog-clutch with actuator, for axial direction/bending motion to be isolated " flexible board " (torque-converters drive disk), the belt pulley with tape handler and/or may by freewheel connect flywheel open Movable tooth circle (" PES ") belongs to this component.
Embodiment with the known clutch 18 from the attached drawing of front is shown, which is constituted herein in Figure 12 For the form of friction clutch, such as multidisc clutch.In order to provide the space for operating clutch 18, bearing 42 and shell The housing wall of body 43 can be pulled to 21 lower section of gear of input shaft 19.For by internal combustion engine 8 be connected to input shaft 19 its In its modification, be also advantageous using the structure space of the lower section of gear 21 of input shaft 19, for example, for freewheel or claw from Clutch.
Figure 13 to 15 shows the illustrative embodiments of the wheel apparatus in internal combustion engine side 14.As already described, interior The gear of the sub- powertrain 2 of combustion engine side is arranged in three wheel planes 9,10 and 16.The big fixation in first round plane 9 It takes turns (corresponding to gear 22 in Fig. 4) to be arranged on input shaft 19, two free gears on jackshaft 23,24 (correspond to It gear 26 in Fig. 4 and 28) is engaged with the fast pulley, the first round plane can also be spatially from internal combustion engine 8 Position (such as seeing in Fig. 4) is exchanged with the second wheel plane 10.In the medium and small fixation of the second wheel plane 10 (referring to Fig.1 4) Wheel (it corresponds to the gear 21 in Fig. 4) is arranged on input shaft 19, and the fast pulley and two on jackshaft 23 and 24 are big Free gear (it corresponds to the gear 25 and 27 in Fig. 4) engagement.The gear 25 and 27 of jackshaft 23,24 leans on very much in Figure 14 Closely, it but does not collide.
Figure 15 shows the shaft device in third round plane 16, and the big output shaft gear 4 of differential mechanism 6 is located at the third round Corresponding to the gear 29,30 in Fig. 4 and 15) it (is engaged, one of gear and jackshaft 23 in plane 16 and with three pinion gears It is fixedly connected, a gear is fixedly connected with jackshaft 24, and third gear mesh answers breast wheel 15, the breast wheel and input shaft Small free gear 44 on 19 engages.
Figure 16 shows the enlarged view of Figure 15, clearly to show the position of axis 19,23,24,15 and 6 or to be formed by it Quadrangle shape, can illustrate the setting of axis to each other by the quadrangle.
The position of axis or by its quadrangle formed shape can by the corresponding angle A, B, C in quadrangle, at D four A angle α, beta, gamma, three in δ illustrate, the 4th angle automatically generates.Together with length data, for example, input shaft 19 with The distance between differential mechanism 6 e or from input shaft 19 to the distance c of jackshaft 23, then determine input shaft 19, jackshaft 23, The axial location of jackshaft 24 and differential mechanism 6 relative to each other.Then in conjunction with zero point and absolute orientation absolutely determine input shaft 19, The axial location of jackshaft 23,24 and differential mechanism 6 being previously mentioned, the zero point are, for example, the central point D of input shaft 19, it is described absolutely To the orientation e.g. gradient of the input shaft 19 towards differential mechanism 6.
Advantageously there are fol-lowing values herein by the interior angle of the obtained quadrangle in the position of axis: at input shaft 19, α= 86 ° (85 ° to 87 °)；At jackshaft 23, β=103 ° (102 ° to 104 °)；At jackshaft 24, (108 ° extremely for γ=109 ° 110°)；At differential mechanism 6, Δ=62 ° (61 ° to 63 °).Distance a to e is advantageous for the car with front lateral gear Ground is with following values: c=106 millimeters (between input shaft 19 and jackshaft 23), d=91 millimeters of (input shaft 19 and jackshafts 24 Between), a=129 millimeters (between jackshaft 23 and differential mechanism 6), b=133 millimeters (between jackshaft 24 and differential mechanism 6), and e =184 millimeters (between input shaft 19 and differential mechanism 6), wherein the distance a to e corresponds to the incline edge lengths or four of quadrangle Other connection line lengths at two angles of side shape.The orientation of quadrangle is advantageously provided (due to the road clearance) in input shaft herein It is 10 ° of the gradient between 19 and differential mechanism 6.
There are two other freedom degree, which can for example retouch the position tool of breast wheel 15 relative to input shaft 19 It states.The center E of breast wheel 15 is preferably provided in the top (axis towards the middle of the connection e between input shaft 19 and differential mechanism 6 23).Thus avoid the collision of the gear 30 of breast wheel 15 and jackshaft 24.
It is exemplified below the example of the out-of-alignment transmission ratio for the first sub- powertrain 2.
Therefore, jackshaft 23 is to the transmission ratios for example about 4.2 to 4.4 of differential mechanism 6 (for example, 74/17,71/16,67/ 16 or similar), transmission ratios for example about 3.7 (such as 74/20,71/19,67/18 or class of the jackshaft 24 to differential mechanism 6 As), and input shaft 19 arrives the transmission ratios for example about 4.1 of differential mechanism 6 (passing through breast wheel 15) (for example, 74/18,71/ 17,67/16 or similar).
In first round plane 9, the transmission ratios for example about 2.1 of input shaft 19 to jackshaft 23 are (for example, 58/28,59/ , and the transmission ratios between input shaft 19 and jackshaft 24 for example about 1.64 (such as 46/28 or similar 28 or similar) ).
Second wheel plane 10 in, input shaft 19 to jackshaft 23 acceleration transmission ratios for example about 0.63 (for example, 32/51,34/51 or similar), the transmission ratios of the acceleration between input shaft 19 and jackshaft 24 for example about 0.41 (such as 21/ 51 or similar).
The gear shift unit of first round plane 9 and the second wheel plane 10 (is not shown in the figure, corresponding to has title in Fig. 3 S1N4, S2N5Shift clutch collar) be located at jackshaft 23 and 24 on.It can be simple sliding sleeve (claw gearshift) or same herein The gear shift unit of step or other frictional fits and/or combined shaped cooperation shifting element.
Figure 17 to 19 shows the illustrative embodiments for supporting breast wheel 15.This shell 43 housing wall advantageously Close vicinity also carrier gear 44 bearing and/or also carry motor 11 (referring to Fig.1 7) or 19 (8 He referring to Fig.1 of input shaft Supporting arrangement Figure 19), the bearing of the housing wall carrying breast wheel 15, the gear 44 can be with input shaft via clutch 20 19 connections.As shown in figure 19, breast wheel 15 is also possible to very short jackshaft 45 when necessary.Here, the bearing of breast wheel 15 The component (for example, housing wall 43 or plate load-bearing part) of device or loading bearing can be set in the tyre side 13 of breast wheel 15, Thus the internal combustion engine side 14 of hybrid powertrain 1 becomes especially short.Alternatively, the supporting arrangement of breast wheel 15 also can be set Second wheel plane 10 and third round plane 16 between internal combustion engine side 14 on or also on two sides distribution be arranged.
Figure 20 is shown for illustrating flow chart or programme diagram from 2 gears to the shift transformation of 3 gears.2 gears are herein in the second wheel It is realized in plane 10 by shape-ordinatedly implementation/realization transmission, and 3 gears are matched via clutch 20 and the friction of breast wheel 15 It is effected or carried out with closing.In first step S1, the torque of internal combustion engine 8 reduces, and wherein the torque of motor 11 increases simultaneously.Once The sliding sleeve engaged with the gear for 2 gears just removes the sliding sleeve not by pulling force, that is, with the gear corresponding to 2 gears (step S2) is unclamped in the connection for transmitting torque.Then, in step s3, advantageously make the revolving speed of internal combustion engine 8 by regulating device It is reduced towards the rotating speed of target of 3 gears.Then, it carries out the engagement of the clutch 20 of 3 gears and there are also at internal combustion engine 8 when necessary The engagement (step S4) of clutch 18.Finally, can be selectively performed the complete or partial of step S1 according to the state of battery Reverse (step S5).
The shift transformation process shown in Figure 20 is (centre) gear from the gear that shape cooperates to frictional fit Shift transformation, and need not forcibly correspond to the transformation from 2 gear, 3 gear, but also can be according to the position of middle apron for example It is the shift transformation from 3 gears to 4 gears, wherein 4 gears then correspond to the middle apron of frictional fit.The gear of shape cooperation is described herein Such as lower gear, torque transmitting is realized via frictional fit in the gear, and the description of the gear of frictional fit passes through frictional fit Realize the gear of torque transmitting.
Figure 21 is shown for describing the flow chart from 4 gears to the shift of 5 gears, wherein shape is distinguished in the two gears Ordinatedly realization/implementation transmission.In first step V1, similar to the step S1 in Figure 20, reduce the torque of internal combustion engine 8, Increase the torque of motor 11 simultaneously.Then, the sliding sleeve engaged with 4 gears is removed, and additionally, if it exists, Clutch 18 is separated into (step V2), so that internal combustion engine 8 be made to separate with input shaft 19, and there is no torques from the biography of internal combustion engine 8 It is delivered on input shaft 19.
As next step (step V3), (for example, passing through regulating device) makes the revolving speed of internal combustion engine 8 towards the target of 5 gears Revolving speed reduces.Once then carrying out synchronizing and being linked into for fifth gear close to the gear, and connecing for clutch 18 is then carried out when necessary It closes (step V4).Torque is transmitted to input shaft 19 from internal combustion engine 8 again as a result,.Finally, according to battery status, optionally Carry out the complete or partial reverse (step V5) of step V1.
Shift transformation process shown in Figure 21 is the gear for the gear that the gear cooperated from shape cooperates to another shape Transformation.4 gears and 5 gears should be regarded as herein to be exemplary, and this method or process can also be for example used in from 1 gear to 2 gears In shift transformation process.
Figure 22 shows the flow chart of the starting of internal combustion engine 8 during illustrating pure electrically driven (operated) traveling, and Figure 23 is described in detail For the step of starting internal combustion engine 8.The process source of graph is the traveling (step Z1) of pure electricity, that is, is transmitted on differential mechanism 6 Torque is only generated by motor 11.If battery capacity is low or speed is high ("Yes" in step Z2 in Figure 22), start internal combustion Machine 8 (step Z3).Then, continue traveling by internal combustion engine 8 or continue in mixed mode in third gear relaying to sail (step Z4).Other shift transformations are related to situation and depend on speed and/or pedal position (step Z5).
However, either low battery capacity the case where or the case where high speed ("No" in Figure 22 in step Z2), all Continue pure electrically driven (operated) traveling (step Z1).
The case where for starting internal combustion engine 8 in step Z3, carry out sub-step shown in Figure 23.In order to start internal combustion engine 8, the clutch 20 of 3 gears is engaged first and at the same time making the moment of friction value (step of the torque raising clutch 20 of motor 11 Z31).Then, once internal-combustion engine rotational speed is more than such as 300 turns/min, internal combustion engine 8 is just activated (injection, igniting etc.).Subsequent Step Z33 in, 3 gear clutches 20 separate, while motor 11 torque reduce (reverse of step Z31).Once internal combustion engine 8 Speed be higher than 3 gear in revolving speed, 3 gear clutches 20 just engage, while motor 11 torque reduce clutch 20 friction The value (step Z34) of torque.Once the skidding on clutch 20 disappears, then the torque of motor 11 finally reduces in step Z35 The torque value (until negative value) of internal combustion engine 8.
Reference signs list
1 hybrid powertrain
2 first sub- powertrain
3 second sub- powertrain
4 output shaft gears
5 final driving wheels
6 differential mechanisms
7 wheels
8 internal combustion engines
9 first round planes
10 second wheel planes
11 motors
12 epicyclic transmission mechanisms
13 tyre sides
14 internal combustion engine sides
15 breast wheels
16 third round planes
17 planet planes
18 clutches
19 input shafts
20 clutches
21 gears
22 gears
23 first jackshafts
24 second jackshafts
25 gears
26 gears
27 gears
28 gears
29 gears
30 gears
31 gear rings
32 planetary gears
33 solar shafts
34 sun gears
35 planet carriers
36 support components
37 shells
38 brakes
39 conversion equipments
40 sliding sleeves
41 torsional vibration dampers
42 bearings
43 shells
44 gears
45 jackshafts
46 shift teeth portion
α, beta, gamma, Δ angle
A, b, c, d, e distance
The angle point of A, B, C, D quadrangle
The central point of E breast wheel

Claims (10)

1. a kind of hybrid powertrain (1), comprising:
Can with the oil-engine driven first sub- powertrain (2), and
Can with the second of motor drive the sub- powertrain (3), wherein
The first sub- powertrain (2) includes the first speed changer, and the second sub- powertrain (3) includes construction At the second speed changer of epicyclic transmission mechanism (12),
The torque of the first sub- powertrain (2) can or by first speed changer or by with it is described first son Powertrain (2) breast wheel (15) coupled that can rub is transmitted on output shaft gear (4), and
The torque of the second sub- powertrain (3) can pass through the planet carrier (35) of epicyclic transmission mechanism (12) and the centre Wheel (15) is transmitted on output shaft gear (4),
It is characterized in that
The geometry setting of the epicyclic transmission mechanism (12) is chosen to, and makes it possible to the gear ring by the epicyclic transmission mechanism (12) (31) torque generated by motor is conveyed.
2. hybrid powertrain (1) according to claim 1, which is characterized in that the first sub- powertrain (2) It is connected to each other in a manner of it can rub and transmit torque with coupling with the described second sub- powertrain (3), and friction clutch Spatially it is arranged between the epicyclic transmission mechanism (12) and the first sub- powertrain (2).
3. hybrid powertrain (1) according to claim 1 or 2, which is characterized in that first transmission configuration at Gear type with gear (21,22,25,26,27,28) has a grade transmission mechanism, and the gear is arranged at first round plane (9) and in the second wheel plane (10).
4. hybrid powertrain (1) according to claim 3, which is characterized in that the transmission ratio of the breast wheel (15) It is poor by two transmission ratios are divided into the transmission ratio difference of second wheel plane (10) from the first round plane (9).
5. hybrid powertrain (1) according to claim 3 or 4, which is characterized in that the first round plane (9) is right Third round should be formed corresponding to 4 gears and 5 gears and the breast wheel (15) and put down in 1 gear and 2 gears, second wheel plane (10) Face (16) and correspond to 3 gear.
6. hybrid powertrain (1) according to any one of claim 1 to 5, which is characterized in that first speed change Device is with the changeable transmission ratio of at least two to the first jackshaft (23) and has to the second jackshaft (24) at least Two changeable transmission ratios.
7. hybrid powertrain (1) according to claim 6, which is characterized in that from the described first sub- powertrain (2) input shaft (19) observation, the angle between first jackshaft (23) and the second jackshaft (24) they are 85 ° to 87 °, with And from output shaft, the angle between first jackshaft (23) and the second jackshaft (24) is 61 ° to 63 °, and from Jackshaft (23, the 24) observation, the angle between the input shaft (19) and the output shaft is 102 ° to 112 °, and institute The central point (E) of breast wheel (15) is stated positioned at the as follows of the connecting line (e) between the input shaft (19) and the output shaft On side: that jackshaft (23) with first gear is located on the side.
8. hybrid powertrain (1) according to any one of claim 1 to 7, which is characterized in that for by torque from The epicyclic transmission mechanism (12) that the motor (11) is transferred to the output shaft is at least partially situated at turning for the motor (11) It is sub internal.
9. hybrid powertrain (1) according to any one of claim 1 to 8, which is characterized in that generated by motor The transmission ratio of torque can switch in the following way: the sun part (34) of the epicyclic transmission mechanism (12) can be with changeable Mode is connect with shell (37) or with another connecting pin of the epicyclic transmission mechanism (12).
10. hybrid powertrain (1) according to any one of claim 1 to 9, which is characterized in that in order to from second Gear transforms to third gear,
The torque that internal combustion engine generates is reduced, while improving the torque of motor generation；
When sliding sleeve is not by pulling force, from second gear dislocation sliding sleeve；
Reduce the revolving speed of internal combustion engine (8) towards the rotating speed of target of third gear；With
It will be engaged in the friction clutch in the torque stream of breast wheel (15).
CN201780054339.1A 2016-09-07 2017-08-31 Hybrid powertrain with intermediate gear Active CN109689411B (en)

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DE102016216991.2A DE102016216991A1 (en) 2016-09-07 2016-09-07 Hybrid powertrain with intermediate gear
DE102016216991.2 2016-09-07
PCT/DE2017/100733 WO2018046058A1 (en) 2016-09-07 2017-08-31 Hybrid drive train having intermediate gear

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